WO2019111714A1 - Damper - Google Patents
Damper Download PDFInfo
- Publication number
- WO2019111714A1 WO2019111714A1 PCT/JP2018/043017 JP2018043017W WO2019111714A1 WO 2019111714 A1 WO2019111714 A1 WO 2019111714A1 JP 2018043017 W JP2018043017 W JP 2018043017W WO 2019111714 A1 WO2019111714 A1 WO 2019111714A1
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- WO
- WIPO (PCT)
- Prior art keywords
- holding chamber
- fluid holding
- peripheral surface
- damper
- width
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/20—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/145—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only rotary movement of the effective parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/369—Sealings for elements other than pistons or piston rods, e.g. valves
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/20—Type of damper
- B60G2202/22—Rotary Damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2224/00—Materials; Material properties
- F16F2224/02—Materials; Material properties solids
- F16F2224/025—Elastomers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/30—Sealing arrangements
Definitions
- the present invention relates to a damper that applies a braking force to an external force by limiting the movement of a viscous fluid.
- a damper that applies a braking force to an external force by limiting the movement of a viscous fluid.
- the damper of this type has an opening and separates the fluid holding chamber for holding the viscous fluid from the fluid holding chamber, and is inserted into the opening of the fluid holding chamber and is inserted relative to the fluid holding chamber by an external force. While partitioning the moving and rotating resistance generating member and the fluid holding chamber, the relative movement or rotation of the resistance generating member relative to the fluid holding chamber compresses one region in the partitioned fluid holding chamber, and
- the apparatus further comprises a capacity changing means for extending the other area, and a flow path for connecting areas in the fluid holding chamber partitioned by the capacity changing means.
- Patent Document 1 discloses a rotary damper that generates a braking torque with respect to an applied rotational force by restricting the movement of a viscous fluid.
- the rotary damper includes a housing having an inner chamber open at one end, a rotor housed in the inner chamber of the housing, a viscous fluid (fluid) filled in the inner chamber of the housing, and an open end of the housing And a plug mounted on the inner side of the housing for containing the viscous fluid.
- the housing and the plug constitute a fluid holding chamber.
- the rotor has a cylindrical rotor body, and movable vanes projecting radially outward from the outer circumferential surface of the rotor body toward the inner circumferential surface of the inner chamber of the housing.
- the rotor main body corresponds to a resistance generating member.
- a fixed vane On the inner circumferential surface of the inner chamber of the housing, a fixed vane is formed which protrudes radially inward toward the outer circumferential surface of the rotor main body and which divides the inner chamber of the housing.
- the stationary vanes constitute capacity changing means together with the movable vanes of the rotor.
- the fixed vanes of the housing are formed with a flow passage (orifice) connecting between the regions of the inner chamber of the housing partitioned by the fixed vanes.
- the bottom of the inner chamber of the housing and the plug are respectively formed with through holes into which the end of the rotor body is rotatably inserted. These through holes correspond to the openings of the fluid holding chamber.
- the rotor is inserted by inserting one end of the rotor body into a through hole formed in the bottom of the inner chamber of the housing and inserting the other end of the rotor body into a through hole formed in the plug,
- the inner chamber of the housing is rotatably accommodated relative to the inner chamber.
- the rotary damper when a rotational force is applied to the rotor and the rotor rotates relative to the inner chamber of the housing, the rotary damper is located upstream of the fixed vanes of the inner chamber in the rotor rotational direction.
- the area located is compressed by the movable vanes and the pressure on the viscous fluid in this area is increased.
- the viscous fluid in this region moves to the region located on the downstream side in the rotor rotational direction with respect to the stationary vanes of the inner chamber via the flow path formed in the stationary vanes.
- a braking torque is generated according to the movement resistance of the viscous fluid (the difficulty of moving the viscous fluid through the flow path).
- the O-ring may be elastically deformed by the external force applied to the resistance generating member, and the center line of the resistance generating member may be eccentric from the center line of the fluid holding chamber to cause an axial deviation.
- it is necessary to increase the rigidity of the O-ring.
- the rigidity of the O ring is increased, the O ring can not elastically deform following movement or rotation of the resistance generating member, and a gap between the resistance generating member and the O ring is generated, and the O ring is held in the fluid holding chamber. The viscous fluid may leak from this gap to the outside.
- the O-ring is circular in cross section, elastic deformation in the radial direction changes the contact area with each of the resistance generating member and the opening of the fluid holding chamber. For this reason, the sealability between the resistance generating member and the opening of the fluid holding chamber becomes unstable, and the possibility of the viscous fluid held in the fluid holding chamber leaking to the outside from this gap further increases.
- the present invention has been made in view of the above circumstances, and an object thereof is to provide a damper capable of more reliably preventing the leakage of the viscous fluid held in the fluid holding chamber.
- a bush is attached to the opening of the fluid holding chamber, and the bush is held slidably by the bush, and the resistance held by the bush Between the force generating member and the opening of the fluid holding chamber, it has a width in the direction of the center line of the fluid holding chamber, and has an outer peripheral surface pressed against the fluid holding chamber and a width in the direction of the center line of the fluid holding chamber And a ring-like elastic member including an inner circumferential surface pressed against the resistance generating member.
- the present invention A damper that generates a braking force against an external force by restricting the movement of a viscous fluid, A fluid holding chamber having an opening and holding the viscous fluid; A resistance generating member inserted into the opening of the fluid holding chamber and moved relative to the fluid holding chamber by the external force; A capacity change which partitions the fluid holding chamber and compresses one region in the partitioned fluid holding chamber and extends the other region with relative movement of the resistance generating member with respect to the fluid holding chamber Means, A flow path connecting between the regions in the fluid holding chamber partitioned by the volume changing means; A bush attached to the opening of the fluid holding chamber and slidably holding the resistance generating member inserted into the opening of the fluid holding chamber; And an annular elastic member disposed between the resistance generating member held by the bush and the opening of the fluid holding chamber.
- the elastic member is An inner circumferential surface having a width in a direction of a center line of the fluid holding chamber and in pressure contact with the resistance generating member; And an outer peripheral surface which has a width in a direction of a center line of the fluid holding chamber and is in pressure contact with the fluid holding chamber.
- the resistance force generation member is slidably held by the bush attached to the opening of the fluid holding chamber, axial displacement of the resistance force generation member is suppressed without increasing the rigidity of the elastic member. be able to. For this reason, the rigidity of the elastic member can be lowered so as to elastically deform following the movement or rotation of the resistance generation member, thereby eliminating the gap between the resistance generation member and the elastic member, and holding the fluid The possibility of the viscous fluid held in the chamber leaking to the outside can be reduced.
- an annular shape having an inner peripheral surface and an outer peripheral surface having a width in the direction of the center line of the fluid holding chamber between the resistance generating member held by the bush and the opening of the fluid holding chamber.
- An elastic member is disposed. For this reason, even when the resistance generating member is axially displaced and the elastic member is elastically deformed in the radial direction, the change in the contact area between each of the openings of the resistance generating member and the fluid holding chamber and the elastic member is reduced. be able to. As a result, the sealability between the opening of the fluid holding chamber and the resistance generating material is stabilized, and the possibility of the viscous fluid held in the fluid holding chamber leaking to the outside can be further reduced.
- FIGS. 1A to 1C are a front view, a side view, and a rear view of a rotary damper 1 according to an embodiment of the present invention.
- 2A is a cross-sectional view of the rotary damper 1 taken along the line AA shown in FIG. 1A
- FIG. 2B is a cross-sectional view taken along the line BB of the rotary damper 1 shown in FIG. is there.
- FIGS. 3A and 3B are an enlarged view of a portion A and an enlarged view of a portion B of the rotary damper 1 shown in FIG. 2A.
- 4 (A) is an enlarged view of a portion C of the rotary damper 1 shown in FIG. 2 (A), and FIG.
- FIG. 4 (B) is an enlarged view of a portion D of the rotary damper 1 shown in FIG. 2 (B).
- 5 (A) is a front view of the case 2
- FIG. 5 (B) is a cross-sectional view of the case 2 shown in FIG. 5 (A) taken along the line CC
- FIG. It is a rear view.
- 6 (A) and 6 (B) are a front view and a side view of the rotor 3
- FIG. 6 (C) is a DD cross-sectional view of the rotor 3 shown in FIG. 6 (A).
- FIGS. 7A and 7B are a side view and a front view of the first and second bushes 4a and 4b
- FIG. 7C shows the first and second bushes shown in FIG. 7B.
- FIG. 5 is a cross-sectional view of the bushes 4a and 4b taken along the line EE.
- 8A and 8B are a front view and a side view of the valve seal 5
- FIG. 8C is a cross-sectional view of the valve seal 5 shown in FIG. .
- 9A to 9C are a front view, a side view, and a rear view of the lid 6,
- FIG. 9D is a GG cross-sectional view of the lid 6 shown in FIG. 9A.
- Fig. 10 (A) is a front view of the first and second seal rings 8a and 8b
- Fig. 10 (B) is a view of H- of the first and second seal rings 8a and 8b shown in Fig. 10 (A).
- FIG. 10 (C) is an enlarged view of a portion E of the first and second seal rings 8a and 8b shown in FIG. 10 (A), and FIG. 10 (B) is FIG. 10 (B). It is the F section enlarged view of the 1st, 2nd seal rings 8a and 8b shown to.
- FIG. 11 (A) is a front view of modified examples 8'a and 8'b of the first and second seal rings 8a and 8b, and FIG. 11 (B) is a modified example 8 shown in FIG. 11 (A).
- FIG. 11 (C) is an enlarged view of a portion G of the modified example 8'a, 8'b shown in FIG. 11 (B).
- FIG. 12 (A) is a side view of a direct acting damper 9 according to another embodiment of the present invention, and FIG. 12 (B) is a side view of the direct acting damper 9 shown in FIG. 12 (A). It is J sectional drawing.
- FIGS. 1A to 1C are a front view, a side view, and a rear view of a rotary damper 1 according to an embodiment of the present invention.
- 2 (A) is a cross-sectional view of the rotary damper 1 taken along the line AA of FIG. 1 (A)
- FIG. 2 (B) is a cross-sectional view of the rotary damper 1 shown in FIG. 1 (B).
- FIG. 3 (A) and 3 (B) are an enlarged view of a portion A and an enlarged view of a portion B of the rotary damper 1 shown in FIG. 2 (A)
- FIG. 4 (A) is a sectional view of FIG. FIG. 4 (B) is an enlarged view of a portion D of the rotary damper 1 shown in FIG. 2 (B).
- the rotary damper 1 according to the present embodiment is required to brake the rotational movement of a rotating body rotating in both directions, such as a seat with a reclining function used in automobiles, railway vehicles, aircraft, ships and the like. Used for the device. As shown, the rotary damper 1 according to the present embodiment is relative to the case 2 and the lid 6, which constitute a fluid holding chamber for holding a viscous fluid (not shown) such as oil or silicone, and the fluid holding chamber. And a rotor 3 rotatably accommodated in the fluid holding chamber.
- FIG. 5 (A) is a front view of the case 2
- FIG. 5 (B) is a cross-sectional view of the case 2 shown in FIG. 5 (A) taken along the line CC
- FIG. It is a rear view.
- a cylindrical chamber (a cylindrical space with a bottom) 21 with one end opened is formed in the case 2, and the bottom 22 of this cylindrical chamber 21 functions as an opening of a fluid holding chamber.
- a through hole 23 for inserting the rotor 3 is formed.
- a first seal ring 8a and a first bush 4a (see FIG. 4A) described later are attached to the through hole 23, and the rotor 3 has a lower end 33a (see FIG. 6) of a rotor main body 31 described later.
- the first seal ring 8 a and the first bush 4 a are axially outward (in the axial direction of the rotary damper 1, in the direction toward the outside of the case 2)
- a step 221 and a step 222 are formed which respectively restrict the movement of
- the cylindrical chamber 21 is projected with the tip end surface 26 in close proximity to the outer peripheral surface 34 (see FIG. 6) of the rotor main body 31 described later of the rotor 3.
- a pair of partitioning portions 25 that partition is formed axially symmetrical with respect to the center line 20 along the center line 20 of the cylindrical chamber 21.
- a female screw portion 27 to be screwed with a male screw portion 62 (see FIG. 9) of the lid 6 described later is formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21, a female screw portion 27 to be screwed with a male screw portion 62 (see FIG. 9) of the lid 6 described later is formed.
- FIG. 6 (A) and 6 (B) are a front view and a side view of the rotor 3, and FIG. 6 (C) is a DD cross-sectional view of the rotor 3 shown in FIG. 6 (A).
- the rotor 3 includes a cylindrical rotor main body 31 and a pair of vanes (rotary blades) 32 formed in axial symmetry with respect to the rotation axis 30 of the rotor main body 31.
- the vanes 32 are formed along the rotation shaft 30 of the rotor 3 and project radially outward from the outer peripheral surface 34 of the rotor main body 31, and the tip end surface 35 approaches the inner peripheral surface 24 of the cylindrical chamber 21 of the case 2. ,
- the cylindrical chamber 21 is divided.
- the vanes 32 together with the partition 25 of the cylindrical chamber 21 of the case 2 constitute capacity changing means for compressing one region in the fluid holding chamber partitioned by the vanes 32 and extending the other region.
- the vane 32 is formed with a flow passage 36 passing between the side surfaces 37 a and 37 b of the vane 32 along the rotational direction of the rotor 3. Further, the valve seal 5 is attached to the vane 32 (see FIG. 2 (B) and FIG. 4 (B)).
- the rotor main body 31 functions as a resistance generating member that rotates relative to the fluid holding chamber by the rotational force from the outside.
- the lower end portion 33a of the rotor main body 31 is rotatably inserted into the through hole 23 formed in the bottom portion 22 of the cylindrical chamber 21 of the case 2 (see FIGS. 2A and 4A).
- the lid 6 is rotatably inserted into a through hole 60 (see FIG. 9) described later (see FIG. 2A, FIG. 3A and FIG. 3B).
- An insertion hole 38 for inserting a 2-chamfered shaft (not shown) for transmitting an external rotational force to the rotor 3 is formed in the rotor body 31 with the rotation shaft 30 as a center.
- the lower end portion 33a of the rotor main body 31 is rotatably inserted into a first seal ring 8a and a first bush 4a described later mounted in the through hole 23 of the cylindrical chamber 21 of the case 2 (see FIG. 4A). ).
- the outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 is axially inward of the first seal ring 8a and the first bush 4a (inward in the axial direction of the rotary damper 1).
- a step 340a is formed to restrict movement.
- the upper end portion 33b of the rotor main body 31 is rotatably inserted in a second seal ring 8b and a second bush 4b mounted in a through hole 60 of the lid 6 described later (FIGS. 3A and 3) (B)).
- a step 340b is formed on the outer peripheral surface 34 of the upper end portion 33b of the rotor body 31 to restrict the axial inward movement of the second seal ring 8b and the second bush 4b.
- FIGS. 7A and 7B are a side view and a front view of the first and second bushes 4a and 4b, and FIG. 7C shows the first and second bushes shown in FIG. 7B.
- FIG. 5 is a cross-sectional view of the bushes 4a and 4b taken along the line EE.
- the first bush 4a and the second bush 4b are cylindrical members formed of a material excellent in slidability, and in the first bush 4a, the lower end portion 33a of the rotor body 31 of the rotor 3 is provided. And the outer peripheral surface 41a in contact with the inner peripheral surface 220a of the through hole 23 of the cylindrical chamber 21 of the case 2 in the second bush 4b. It has an inner circumferential surface 40b in sliding contact with the outer circumferential surface 34 of the upper end 33b of the rotor main body 31, and an outer circumferential surface 41b in contact with the inner circumferential surface 64 (see FIG. 9D) of the through hole 60 of the lid 6.
- the first bush 4a and the second bush 4b are formed of metal such as brass alloy or synthetic resin such as PTFE (polytetrafluoroethylene), polyacetal resin, polyethylene resin, polyamide resin, polyphenylene sulfide resin and the like.
- a multi-layer sliding member in which a plurality of sliding layers are formed may be formed on the inner circumferential surface of a back member such as a cylindrical steel plate or resin composite.
- a multilayer sliding member in which a sintered metal layer is formed on the inner circumferential surface of a back member made of a cylindrical steel plate and a resin sliding layer containing PTFE is further formed thereon.
- FIG. 8A and 8B are a front view and a side view of the valve seal 5, and FIG. 8C is a cross-sectional view of the valve seal 5 shown in FIG. .
- the valve seal 5 has a U-shape that can be attached to the vane 32 of the rotor 3 and has a width t2 longer than the width t1 (see FIG. 6A) of the vane 32 in the rotational direction.
- a bottom portion 50, and one end 51 of the bottom portion 50 integrally formed, and having a width t4 longer than a radial width t3 (see FIG. 6B) of the flow path 36 formed in the vane 32
- One leg 53 and a second leg 54 integrally formed at the other end 52 of the bottom 50 and having a width t5 shorter than the radial width t3 of the flow passage 36 formed in the vane 32; Have.
- valve seal 5 mounted on the vane 32 closes these gaps by the bottom 50 being interposed between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21 of the case 2 (FIG. B) see). Further, as shown in FIG. 2B, when the rotor 3 rotates in the first rotational direction R1 relative to the cylindrical chamber 21 of the case 2, the first leg 53 of the valve seal 5 is one of the vanes 32. Abuts against the side surface 37a of the vane 32 to block the flow passage 36 formed in the vane 32.
- valve seal 5 is disposed between the case 2 and the rotor 3 which are relatively rotated, it is preferable to use a material excellent in slidability, for example, a synthetic resin such as a polyamide resin.
- FIG. 9A to 9C are a front view, a side view, and a rear view of the lid 6, and FIG. 9D is a GG cross-sectional view of the lid 6 shown in FIG. 9A. It is.
- the lid 6 has a through hole 60 for inserting the rotor 3 which functions as an opening of the fluid holding chamber at a position facing the through hole 23 formed in the bottom 22 of the cylindrical chamber 21 of the case 2. It is formed.
- a second seal ring 8b and a second bush 4b (see FIG. 3A) described later are attached to the through hole 60, and the upper end 33b of the rotor main body 31 of the rotor 3 is the second seal ring 8b and The second bush 4b is inserted into the through hole 60 mounted.
- the inner circumferential surface 64 of the through hole 60 is formed with a step 65 and a step 66 which respectively restrict the outward movement of the second seal ring 8 b and the second bush 4 b in the axial direction.
- a male screw portion 62 to be screwed with the female screw portion 27 formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21 is formed on the outer peripheral surface 61 of the lid 6, a male screw portion 62 to be screwed with the female screw portion 27 formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21 is formed.
- a groove 67 for mounting the O-ring 7 is formed in the circumferential direction. The O-ring 7 is mounted in the groove 67 and is interposed between the outer peripheral surface 61 of the lid 6 and the inner peripheral surface 24 of the cylindrical chamber 21, and the male screw 62 of the lid 6 and the female screw 27 of the cylindrical chamber 21. And prevent the viscous fluid from leaking out of the screwed portion (see FIGS. 3A and 3B).
- Fig. 10 (A) is a front view of the first and second seal rings 8a and 8b
- Fig. 10 (B) is a view of H- of the first and second seal rings 8a and 8b shown in Fig. 10 (A).
- 10 (C) is an enlarged view of a portion E of the first and second seal rings 8a and 8b shown in FIG. 10 (A)
- FIG. 10 (B) is FIG. 10 (B). It is the F section enlarged view of the 1st, 2nd seal rings 8a and 8b shown to.
- first seal ring 8a and the second seal ring 8b are annular members formed of an elastic body such as nitrile butadiene rubber (NBR), and in the first seal ring 8a, the rotor of the rotor 3 is
- the second seal has an inner diameter d1 smaller than the outer diameter d4 of the lower end portion 33a of the main body 31, and an outer diameter d2 larger than the inner diameter d3 of the through hole 23 of the cylindrical chamber 21 of the case 2 (the outer diameter of the step 221).
- the ring 8b has an inner diameter d1 smaller than the outer diameter d5 of the upper end 33b of the rotor body 31 of the rotor 3 and an outer diameter d2 larger than the inner diameter d5 of the through hole 60 of the lid 6 (the outer diameter of the step 65).
- the first seal ring 8 a and the second seal ring 8 b have an inner circumferential side annular portion 81 having a rectangular cross section, an outer circumferential side annular portion 82 having a rectangular cross section, and a connecting portion 83.
- the inner circumferential side annular portion 81 has an inner circumferential surface 84 having a flat width t6 in the direction of the center line 80 coinciding with the center line 20 of the cylindrical chamber 21 of the case 2.
- the inner peripheral surface 84 has a flat width t6 in the direction of the center line 80, the contact between the inner peripheral surface 84 and the mating surface when the first seal ring 8a and the second seal ring 8b are elastically deformed in the radial direction. A change in area can be suppressed.
- the inner peripheral surface 84 is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 of the rotor 3 in the first seal ring 8a, and the upper end 33b of the rotor main body 31 of the rotor 3 in the second seal ring 8b.
- the outer circumferential surface 34 of the Further, a grease groove 86 is formed in the circumferential direction on the inner circumferential surface 84, and the grease is filled in the grease groove 86. Although one grease groove 86 in the circumferential direction is formed in the inner circumferential surface 84 here, a plurality of grease grooves 86 in the circumferential direction may be formed in the inner circumferential surface 84.
- the outer circumferential side annular portion 82 has an outer circumferential surface 85 having a flat width t7 in the direction of the center line 80 which coincides with the center line 20 of the cylindrical chamber 21 of the case 2. Since the outer peripheral surface 85 has a flat width t7 in the direction of the center line 80, the contact area between the outer peripheral surface 85 and the mating surface when the first seal ring 8a and the second seal ring 8b are elastically deformed in the radial direction. Change can be suppressed.
- the outer circumferential surface 85 is in pressure contact with the inner circumferential surface 220 of the through hole 23 of the cylindrical chamber 21 of the case 2 in the first seal ring 8a, and the inner circumferential surface of the through hole 60 of the lid 6 in the second seal ring 8b. Press into contact with 64.
- the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81 is narrower than the width t7 of the outer circumferential surface 85 of the outer circumferential side annular portion 82 (t6 ⁇ t7). For this reason, the frictional resistance of the inner circumferential surface 84 of the inner circumferential side annular portion 81 becomes smaller than the frictional resistance of the outer circumferential surface 85 of the outer circumferential side annular portion 82. Therefore, when the rotor 3 is rotated relative to the cylindrical chamber 21 of the case 2, the inner peripheral surface 84 of the rotor 3 is in pressure contact with the inner peripheral surface 84 of the inner peripheral side annular portion 81 having a low coefficient of friction.
- the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81 is the outer circumferential side annular portion It is preferable to set t7 / t6 ⁇ 3 with respect to the width t7 of the outer peripheral surface 85 of 82.
- the width t7 of the outer circumferential surface 85 of the outer circumferential side annular portion 82 is too long relative to the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81, and the outer circumferential side annular portion
- the end portion of the outer peripheral surface 85 of 82 may be bent radially inward, and a desired sealing performance may not be obtained. Also, the installation space of the first seal ring 8a and the second seal ring 8b is increased.
- the width of the grease groove 86 provided on the inner circumferential surface 84 of the inner circumferential side annular portion 81 is equal to 0. 0. with respect to the width t6 of the inner circumferential surface 84 of the inner circumferential annular portion 81. It is preferable that 05 ⁇ t9 / t6 ⁇ 0.5.
- connecting portion 83 is disposed between the inner peripheral side annular ring portion 81 and the outer peripheral side annular portion 82 to connect the both. Further, in the direction of center line 80, connecting portion 83 has a width (width of inner circumferential surface 84) t6 of inner circumferential side annular portion 81 and a width (width of outer circumferential surface 85) t7 of outer circumferential side annular portion 82. Also has a narrow width t8 (t8 ⁇ t6 ⁇ t7).
- the connecting portion 83 is elastically deformed to absorb the stress, thereby the inner circumferential side annular portion 81 and the outer circumferential side annular ring Elastic deformation of the portion 82 is suppressed.
- the width t 8 of the connecting portion 83 is relative to the width t 6 of the inner circumferential annular portion 81 Preferably, 0.3 ⁇ t8 / t6 ⁇ 0.95.
- t8 / t6 is smaller than 0.3, the rigidity of the connecting portion 83 is reduced, and the outer peripheral surface of the lower end portion 33a or the upper end portion 33b of the rotor body 31 of the rotor 3 of the inner peripheral surface 84 of the inner peripheral side annular portion 81 The pressing force against 34 becomes too weak and the sealing performance is reduced.
- the movement of the viscous fluid filled in the cylindrical chamber 21 is determined by the gap g1 between the tip surface 26 of the partition 25 of the cylindrical chamber 21 of the case 2 and the outer peripheral surface 34 of the rotor main body 31 of the rotor 3.
- the gap g2 between the upper surface 29 and the lower surface 63 of the lid 6 and the gap g3 between the lower surface 63 of the lid 6 and the upper surface 38 of the vane 32 of the rotor 3 are limited only (Figs. 3A and 3). (See (B))
- the pressure on the viscous fluid in the area 21a (see FIG. 2B) divided by the vane 32 and the partition 25 positioned on the first rotational direction R1 side with respect to the vane 32 is increased. For this reason, a strong braking torque is generated.
- the rotor 3 is slidably held by the first bush 4 a and the second bush 4 b attached to the through hole 23 of the cylindrical chamber 21 of the case 2 and the through hole 60 of the lid 6 respectively. Therefore, the axial displacement of the rotor 3 can be suppressed without increasing the rigidity of the first seal ring 8a and the second seal ring 8b that slidably holds the rotor 3 together with the first bush 4a and the second bush 4b. Can.
- the rigidity of the first seal ring 8a and the second seal ring 8b can be lowered so as to elastically deform following the rotation of the rotor 3, whereby the rotor 3 and the first seal ring 8a and the second
- the possibility of the viscous fluid held in the cylindrical chamber 21 of the case 2 leaking to the outside can be reduced.
- the flat width t7 in the direction of the center line 20 of the cylindrical chamber 21 is provided between the through-hole 23 of the cylindrical chamber 21 of the case 2 and the lower end 33a of the rotor main body 31 of the rotor 3. And has a flat width t6 in the direction of the center line 20 of the cylindrical chamber 21 and is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor body 31.
- the rotor 3 is axially offset and the first and second seal rings 8a and 8b are The contact area between the first seal ring 8a and the lower end portion 33a of the rotor body 31, the contact area between the first seal ring 8a and the through hole 23 of the cylindrical chamber 21, and the second seal ring 8b when elastically deformed in the radial direction. It is possible to suppress changes in the contact area between the upper end portion 33b of the rotor main body 31 and the contact area between the second seal ring 8b and the through hole 60 of the lid 6.
- the width t6 of the inner peripheral surface 84 of the first and second seal rings 8a and 8b is smaller than the width t7 of the outer peripheral surface 85.
- the grease groove 86 is formed in the circumferential direction on the inner peripheral surface 84 of the first and second seal rings 8a and 8b, and the grease groove 86 is filled with the grease. For this reason, it is possible to make the rotor 3 slide more smoothly by reducing the frictional resistance between the first and second seal rings 8a and 8b and the rotor 3.
- the first and second seal rings 8 a and 8 b have an outer circumferential side having a rectangular cross section including an inner circumferential surface 84 and an outer circumferential side having a rectangular cross section including an outer circumferential surface 85.
- An annular portion 82 and a connecting portion 83 for connecting the inner circumferential side annular portion 81 and the outer circumferential side annular portion 82 are provided.
- the connecting portion 83 is in the direction of the center line 20 of the cylindrical chamber 21. It has a width t8 narrower than the inner circumferential side annular portion 81 and the outer circumferential side annular portion 82.
- the connecting portion 82 is elastically deformed to absorb the stress, thereby the inner circumferential side annular portion 81 and the outer circumferential side annular portion
- the elastic deformation of the first seal ring 8a and the lower end portion 33a of the rotor main body 31 is suppressed, the contact area of the first seal ring 8a and the through hole 23 of the cylindrical chamber 21 and the second seal ring 8b. It is possible to further suppress changes in the contact area with the upper end portion 33 b of the rotor main body 31 and the contact area between the second seal ring 8 b and the through hole 60 of the lid 6.
- the sealing performance between the through hole 23 of the cylindrical chamber 21 and the lower end 33a of the rotor main body 31, and between the through hole 60 of the lid 6 and the upper end 33b of the rotor main body 31 is further stabilized.
- the possibility that the viscous fluid filled in the chamber 21 leaks from these gaps can be further reduced.
- the step 221 and the outward movement of the first seal ring 8a and the first bush 4a are restricted.
- a step 222 is formed, and a step 340a is formed on the outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 to restrict the axially inward movement of the attached first seal ring 8a and the first bush 4a.
- the inner circumferential surface 64 of the through hole 60 of the lid 6 is provided with a step 65 and a step 66 for restricting the outward movement of the second seal ring 8b and the second bush 4b in the axial direction.
- a step 340b is formed on the outer peripheral surface 34 of the upper end portion 33b of the rotor main body 31 to restrict the axial inward movement of the second seal ring 8b and the second bush 4b.
- the valve seal 5 slidably supports the outer peripheral surface 34 of the rotor main body 31 of the rotor 3 by using the resin having excellent slidability such as polyamide for the valve seal 5. Since it functions as a slide bearing, it is possible to smoothly rotate the shaft by absorbing rattling due to eccentricity or the like of the shaft that transmits the rotational force from the outside to the rotor 3 together with the first bush 4a and the second bush 4b. .
- the first bush 4a is disposed axially outward with respect to the first seal ring 8a (see FIGS. 2A and 4A). 4a may be disposed axially inward with respect to the first seal ring 8a.
- the second bush 4b is disposed axially outward with respect to the second seal ring 8b (FIG. 2 (A), FIG. 3 (A) and FIG. 3 (B). ), The second bush 4b may be disposed axially inward with respect to the second seal ring 8b.
- the first bush 4a and the second bush 4b are lubricated with the viscous fluid held in the cylindrical chamber 21 of the case 2 by holding the viscous fluid having excellent lubricity in the cylindrical chamber 21 of the case 2.
- the rotor 3 can be rotatably held more smoothly.
- the outer peripheral side annular portion 81 having a rectangular cross section including the inner peripheral surface 84 and the outer periphery having a rectangular cross section including the outer peripheral surface 85
- the first and second seal rings 8a and 8b have an inner circumferential surface 84 having a width t6 in the direction of the center line 20 of the cylindrical chamber 21 and an outer circumferential surface 85 having a width t7 in the direction of the center line 20 of the cylindrical chamber 21 , As long as it is provided.
- it may be an annular member having a rectangular cross-section including the inner circumferential surface 84 and the outer circumferential surface 85.
- the width t6 of the inner circumferential surface 84 of the first and second seal rings 8a and 8b is made narrower than the width t7 of the outer circumferential surface 85, and the inner circumferential surface 84 slides against the mating surface. It is causing However, the present invention is not limited to this.
- the width t7 of the outer peripheral surface 85 of the first and second seal rings 8a and 8b may be smaller than the width t6 of the inner peripheral surface 84 to cause the outer peripheral surface 85 to slide with the mating surface.
- the grease grooves 86 are formed in the circumferential direction on the inner peripheral surfaces 84 of the first and second seal rings 8a and 8b, and the grease grooves 86 are filled with the grease.
- the present invention is not limited to this.
- a grease groove is formed in the circumferential direction on at least one of the inner peripheral surface 84 and the outer peripheral surface 85 of the first and second seal rings 8a and 8b which slide with the mating surface, and the grease groove is filled with the grease. Just do it.
- the inner peripheral surface 84 and the outer peripheral surface 85 of the first and second seal rings 8a and 8b are flat in the direction of the center line 20 of the cylindrical chamber 21, but the present invention It is not limited to this.
- the inner circumferential surface 84 and the outer circumferential surface 85 of the first and second seal rings 8 a and 8 b may have a width in the direction of the center line 20 of the cylindrical chamber 21.
- FIG. 11 (A) is a front view of modified examples 8'a and 8'b of the first and second seal rings 8a and 8b
- FIG. 11 (B) is a modified example 8 shown in FIG. 11 (A)
- FIG. 11 (C) is an enlarged view of a portion G of the modified example 8'a, 8'b shown in FIG. 11 (B).
- the modifications 8'a and 8'b are annular members formed of an elastic body such as nitrile butadiene rubber, and the modifications of the first seal ring 8a.
- the outer diameter is larger than the inner diameter d1 smaller than the outer diameter d4 of the lower end 33a of the rotor body 31 of the rotor 3 and the inner diameter d3 of the through hole 23 of the cylindrical chamber 21 of the case 2 (the outer diameter of the step 221).
- modifications 8'a and 8'b have an inner circumferential surface 84 'having a width t6 in the direction of center line 80 and an outer circumferential surface 85' having a width t7 in the direction of center line 80.
- the width t6 of the inner circumferential surface 84 'and the width t7 of the outer circumferential surface 85' are the same, but both may be different.
- the inner circumferential surface 84 ' has a radius r1 longer than half the radial width t10 of the modified examples 8'a and 8'b in the direction of the center line 80 coinciding with the center line 20 of the cylindrical chamber 21 of the case 2.
- the modified example 8'a of the first seal ring 8a it is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor body 31 of the rotor 3, and the modified example 8'b of the second seal ring 8b In this case, the outer peripheral surface 34 of the upper end portion 33 b of the rotor body 31 of the rotor 3 is in pressure contact.
- the outer peripheral surface 85 ' is an arc-shaped surface having a radius r2 longer than half the radial width t10 of the modified examples 8'a and 8'b in the direction of the center line 80, and the first seal
- the inner peripheral surface 220 of the through hole 23 of the cylindrical chamber 21 of the case 2 is in pressure contact
- the modified example 8'b of the second seal ring 8b the inside of the through hole 60 of the lid 6 The pressure is applied to the circumferential surface 64.
- the curvatures of the inner circumferential surface 84 'and the outer circumferential surface 85' can be made smaller than O-rings that can be substituted for the modified examples 8'a and 8'b. Therefore, it is possible to suppress a change in the contact area between each of the inner peripheral surface 84 'and the outer peripheral surface 85' and the other surface when the modified examples 8'a and 8'b are elastically deformed in the radial direction Can be improved.
- the case where the pair of partition portions 25 is provided in the cylindrical chamber 21 and the pair of vanes 32 is provided in the rotor 3 has been described as an example.
- the present invention is not limited to this.
- the partitions 25 formed in the cylindrical chamber 21 and the vanes 32 formed in the rotor 3 have the same number, one or three or more may be formed.
- the valve seal 5 mounted on the vane 32 has the function of a check valve for opening and closing the flow passage 36 formed in the vane 32.
- the present invention is limited thereto I will not.
- the non-return valve may be provided separately from the valve seal 5 to open the flow path 36 formed in the vane 32 when it rotates.
- the flow path 36 which penetrates the both sides 37a and 37b of the vane 32 in the said embodiment along the rotation direction of the rotor 3 is formed in the vane 32
- this invention is not limited to this.
- flow paths may be formed in the partition 25 along both sides of the partition 25 along the rotational direction of the rotor 3.
- a check valve may be provided that opens the flow path formed in the partition 25.
- the first leg is integrally formed with the first portion and has a width longer than the radial width of the flow path formed in the partition 25, and the other end of the bottom is integrally formed with the partition 25
- a sealing material having a second leg portion having a width shorter than the radial width of the formed flow path may be attached to the partition portion 25.
- the first leg of the seal material abuts on one side surface of the partition 25 and is formed in the partition 25
- the first leg of the seal member is separated from one side of the partition 25, and the second leg is partitioned It abuts on the other side surface of the portion 25 to open the flow path formed in the partition portion 25.
- valve seal 5 When the flow passage 36 is not formed in the vane 32, the valve seal 5 may have any shape as long as it can close the gap between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21. It may be Also, the valve seal 5 may be omitted.
- the female screw portion 27 is formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21, and the male screw portion screwed with the female screw portion 27 on the outer peripheral surface 61 of the lid 6.
- the lid 6 is attached to the case 2 by forming 62.
- the present invention is not limited to this.
- the lid 6 may be bolted to the case 2 or riveted. Alternatively, they may be attached by welding, an adhesive or the like.
- the rotor 3 is rotated relative to the cylindrical chamber 21 of the case 2 by applying a rotational force to the rotor 3 from the outside.
- the rotor 3 may be rotated relative to the cylindrical chamber 21 of the case 2 by applying a rotational force to the case 2 from the outside.
- the movement resistance of the viscous fluid flowing in the flow path formed in the vane 32 or the partition 25 in both the first rotational direction R1 and the second rotational direction R2 (the movement of the viscous fluid through the flow path is difficult) can be applied to a so-called bidirectional rotary damper that generates a braking torque according to the
- the valve seal 5 does not require the function of the check valve.
- the valve seal 5 only needs to be able to close the gap between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21. Also, the valve seal 5 may be omitted.
- the rotary damper 1 which generates the braking torque with respect to the rotational force applied from the outside by limiting the movement of the viscous fluid has been described as an example.
- the present invention is not limited to this.
- the present invention is widely applicable to a damper that generates a braking force against an external force by limiting the movement of a viscous fluid.
- FIG. 12 (A) is a side view of a direct acting damper 9 according to another embodiment of the present invention
- FIG. 12 (B) is a side view of the direct acting damper 9 shown in FIG. 12 (A). It is J sectional drawing.
- the linear motion damper 9 is used for a chair with a height adjustment function, a movable shelf, and other devices that are required to brake the linear motion of a moving object.
- the linear motion damper 9 includes a case 920 and a lid 960 which constitute a fluid holding chamber for holding a viscous fluid (not shown) such as oil and silicone, and the direction of the center line 902 with respect to the fluid holding chamber. And a shaft 930 accommodated in the fluid holding chamber so as to be linearly movable relative thereto.
- a cylindrical chamber (a cylindrical space with a bottom) 921 having one end opened is formed, and an insertion hole 923 for insertion of the shaft 930 is formed in the bottom 922 of the cylindrical chamber 921.
- the first seal ring 980a and the first bush 990a are mounted in the insertion hole 923, and the shaft 930 is mounted at one end 933a of the shaft main body 931 described later on the first seal ring 980a and the first bush 990a.
- a mounting portion 927 for mounting the first seal ring 980a and the first bush 990a is formed in a stepped annular groove shape. Further, in the bottom 925 of the insertion hole 923, a through hole 926 for air removal is formed. Further, a lid 960 is attached to the opening side 928 of the inner circumferential surface 924 of the cylindrical chamber 921 by screwing, bonding, welding, screwing, screwing, or the like.
- the shaft 930 includes a cylindrical shaft body 931 and a flange 932 formed near the center of the shaft body 931.
- the flange 932 protrudes radially outward from the outer peripheral surface 934 of the shaft main body 931 near the center of the shaft main body 931, and the tip end surface 935 approaches the inner peripheral surface 924 of the cylindrical chamber 921 of the case 920.
- the flange 932 forms a capacity changing means for compressing one area in the cylindrical chamber 921 partitioned by the flange 932 and extending the other area in accordance with the linear movement of the shaft 930 in the direction of the center line 903.
- a flow path 936 is formed along the direction of the center line 903 of the shaft 930 and between the side surfaces 937a and 937b of the flange 932.
- the flow path 936 is closed, and a second movement direction L2 opposite to the first movement direction L1.
- the valve 970 is attached to open the flow passage 936.
- the outer peripheral surface 935 of the flange 932 forms a gap g ′ that functions as a flow path of the viscous fluid filled in the cylindrical chamber 921 between the outer peripheral surface 935 and the inner peripheral surface 924 of the cylindrical chamber 921 of the case 920.
- the shaft main body 931 functions as a resistance generating member that moves in the direction of the center line 902 of the cylindrical chamber 921 relative to the cylindrical chamber 921 by an external force in the direction of the center line 903 of the shaft 930.
- Shaft body 931 has one end 933a side inserted in insertion hole 923 formed in bottom 922 of cylindrical chamber 921 of case 920 so as to be movable in the direction of center line 902 of cylindrical chamber 921 and the other end
- the 933 b side is movably inserted into the through hole 961 of the lid 960 in the direction of the center line 902 of the cylindrical chamber 921.
- the lid 960 is formed with a through hole 961 for insertion of a shaft 930 functioning as an opening of the fluid holding chamber at a position opposite to the insertion hole 923 formed in the bottom 922 of the cylindrical chamber 921 of the case 920.
- the second seal ring 980b and the second bush 990b are mounted in the through hole 961, and the shaft 930 has the other end 933b of the shaft body 931 mounted on the second seal ring 980b and the second bush 990b. It is inserted into the through hole 961.
- a mounting portion 962 for mounting the second seal ring 980 b and the second bush 990 b is formed in a stepped annular groove shape on the inner peripheral surface 964 of the through hole 961.
- the first bush 990 a and the second bush 990 b are cylindrical members formed of a material having excellent slidability, and the inner circumference of the first bush 990 a slidably contacts the outer peripheral surface 934 of the shaft main body 931 of the shaft 930. And an outer peripheral surface in contact with the inner peripheral surface 929 of the insertion hole 923 of the cylindrical chamber 921 of the case 920, and the second bush 990b is in sliding contact with the outer peripheral surface 934 of the shaft main body 931 of the shaft 930. It has a circumferential surface and an outer circumferential surface in contact with the inner circumferential surface 964 of the through hole 961 of the lid 960.
- the first bush 990a and the second bush 990b are formed of, for example, a metal such as a brass alloy or a synthetic resin such as PTFE, polyacetal resin, polyethylene resin, polyamide resin, polyphenylene sulfide resin.
- a multi-layer sliding member may be formed in which a plurality of sliding layers formed by impregnating a woven or non-woven fabric with a synthetic resin such as phenol resin are formed on the inner peripheral surface of a cylindrical back metal. .
- the first and second seal rings 980a and 980b are annular members formed of an elastic material such as nitrile butadiene rubber.
- the first seal ring 980 a has a width in the direction of the center line 902 of the cylindrical chamber 921 and is in contact with the outer peripheral surface 934 of the shaft body 931 slidably and in the direction of the center line 902 of the cylindrical chamber 921. And an outer peripheral surface pressed against the groove bottom of the mounting portion 927 formed on the inner peripheral surface 929 of the insertion hole 923 of the case 920.
- the second seal ring 980 b has a width in the direction of the center line 902 of the cylindrical chamber 921, and an inner circumferential surface slidably pressed against the outer circumferential surface 934 of the shaft main body 931, and a center line 902 of the cylindrical chamber 921. And the outer peripheral surface of the mounting portion 962 formed on the inner peripheral surface 964 of the through hole 961 of the lid 960 in pressure contact with the groove bottom.
- the first and second seal rings 980a and 980b for example, the first and second seal rings 8a and 8b shown in FIG. 10 or the deformations of the first and second seal rings 8a and 8b shown in FIG. Examples 8'a, 8'b, etc. can be used.
- the check valve 970 blocks channel 936. Therefore, the movement of the viscous fluid filled in the cylindrical chamber 921 is limited only by the gap g ′ between the outer peripheral surface 935 of the flange 932 of the shaft 930 and the inner peripheral surface 924 of the cylindrical chamber 921. In contrast, the pressure on the viscous fluid in the region 921a on the first movement direction L1 side is increased. For this reason, a strong braking torque is generated.
- the check valve 970 opens the flow path 936 . Therefore, in addition to the gap g ′ between the outer peripheral surface 935 of the flange 932 and the inner peripheral surface 924 of the cylindrical chamber 921, the movement of the viscous fluid filled in the cylindrical chamber 921 adds the flow passage 936 formed in the flange 932 Since the pressure is applied to the viscous fluid in the area 921b on the second movement direction L2 side with respect to the flange 932, the shaft 930 moves in the first movement direction L1 relative to the cylindrical chamber 921 of the case 920. Not as high as when Therefore, a braking torque that is weaker than when the shaft 930 moves in the first movement direction L1 relative to the cylindrical chamber 921 of the case 920 is generated.
- the shaft 930 is slidably held by the first bush 990a and the second bush 990b which are attached to the insertion hole 923 of the cylindrical chamber 921 of the case 920 and the through hole 961 of the lid 960 respectively. Since the first seal ring 980a and the second seal ring 980b, which slidably hold the shaft 930 together with the first and second bushes 990a and 990b, do not make the shaft 930 off-axis without increasing its rigidity. It can be suppressed.
- the rigidity of the first seal ring 980a and the second seal ring 980b can be lowered to elastically deform following the movement of the shaft 930, whereby the shaft 930 and the first seal ring 980a and the second
- the possibility of the viscous fluid held in the cylindrical chamber 921 of the case 920 leaking to the outside can be reduced.
- a first seal ring 980a having an outer peripheral surface pressed against the groove bottom of the formed mounting portion 927 is disposed, and a cylinder is provided between the through hole 961 of the lid 960 and the other end 933b of the shaft main body 931.
- the cover 960 has a width in the direction of the center line 902 of the chamber 921 and has a width in the direction of the center line 902 of the cylindrical chamber 921. Penetration of It is arranged and the outer circumferential surface of the groove bottom and pressing the mounting portion 962 inner peripheral surface 964 formed in the hole 961, the second seal ring 980b having.
- the shaft 930 is offset and the first and second seal rings 980a and 980b have diameters.
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Abstract
This rotary damper (1) comprises: a first seal ring (8a) arranged between a through-hole (23) in a cylindrical chamber (21) of a case (2) and the bottom end (33a) of a rotor body (31) of a rotor (3); a first bushing (4a); a second seal ring (8b) arranged between a through-hole (60) in a lid (6) and the upper end (33b) of the rotor body (31); and a second bushing (4b). The first seal ring (8b) has an outer peripheral surface (85) having width in the centerline direction of the cylindrical chamber (21) and pressing against the inner peripheral surface (220) of the through-hole (23), and an inner peripheral surface (84) having width in the centerline direction of the cylindrical chamber (21) and pressing against the outer peripheral surface (34) of the lower end (33a). The second seal ring (8b) comprises an outer peripheral surface (85) having width in the centerline direction of the cylindrical chamber (21) and pressing against the inner peripheral surface (64) of the through-hole (60), and an inner peripheral surface (84) having width in the centerline direction of the cylindrical chamber (21) and pressing against the outer peripheral surface (34) of the lower end (33a).
Description
本発明は、粘性流体の移動を制限することにより、外力に対して制動力を付与するダンパに関する。
The present invention relates to a damper that applies a braking force to an external force by limiting the movement of a viscous fluid.
粘性流体の移動を制限することにより、外力に対して制動力を付与するダンパが知られている。この種のダンパは、開口部を有し、粘性流体を保持する流体保持室と、流体保持室内を仕切るとともに、流体保持室の開口部に挿入され、外力により流体保持室に対して相対的に移動あるいは回転する抵抗力発生部材と、流体保持室内を仕切るとともに、流体保持室に対する抵抗力発生部材の相対的な移動あるいは回転に伴い、仕切られた流体保持室内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段と、容量変更手段によって仕切られた流体保持室内の領域間を連結する流路と、を備えている。
A damper is known that applies a braking force to an external force by limiting the movement of a viscous fluid. The damper of this type has an opening and separates the fluid holding chamber for holding the viscous fluid from the fluid holding chamber, and is inserted into the opening of the fluid holding chamber and is inserted relative to the fluid holding chamber by an external force. While partitioning the moving and rotating resistance generating member and the fluid holding chamber, the relative movement or rotation of the resistance generating member relative to the fluid holding chamber compresses one region in the partitioned fluid holding chamber, and The apparatus further comprises a capacity changing means for extending the other area, and a flow path for connecting areas in the fluid holding chamber partitioned by the capacity changing means.
例えば、特許文献1には、粘性流体の移動を制限することにより、加えられた回転力に対して制動トルクを発生させるロータリダンパが開示されている。このロータリダンパは、一端が開口した内室を備えたハウジングと、ハウジングの内室に収容されたロータと、ハウジングの内室に充填された粘性流体(流動体)と、ハウジングの開口側端部に取り付けられてハウジングの内室に充填された粘性流体を封じ込めるプラグと、を備える。ハウジングおよびプラグは、流体保持室を構成する。
For example, Patent Document 1 discloses a rotary damper that generates a braking torque with respect to an applied rotational force by restricting the movement of a viscous fluid. The rotary damper includes a housing having an inner chamber open at one end, a rotor housed in the inner chamber of the housing, a viscous fluid (fluid) filled in the inner chamber of the housing, and an open end of the housing And a plug mounted on the inner side of the housing for containing the viscous fluid. The housing and the plug constitute a fluid holding chamber.
ロータは、円筒形状のロータ本体と、ハウジングの内室の内周面に向けてロータ本体の外周面から径方向外方に突出した可動ベーンと、を有する。ロータ本体は、抵抗力発生部材に相当する。
The rotor has a cylindrical rotor body, and movable vanes projecting radially outward from the outer circumferential surface of the rotor body toward the inner circumferential surface of the inner chamber of the housing. The rotor main body corresponds to a resistance generating member.
ハウジングの内室の内周面には、ロータ本体の外周面に向けて径方向内方に突出し、ハウジングの内室を仕切る固定ベーンが形成されている。固定ベーンは、ロータの可動ベーンとともに容量変更手段を構成する。
On the inner circumferential surface of the inner chamber of the housing, a fixed vane is formed which protrudes radially inward toward the outer circumferential surface of the rotor main body and which divides the inner chamber of the housing. The stationary vanes constitute capacity changing means together with the movable vanes of the rotor.
ハウジングの固定ベーンには、この固定ベーンによって仕切られるハウジングの内室の領域間を繋ぐ流路(オリフィス)が形成されている。
The fixed vanes of the housing are formed with a flow passage (orifice) connecting between the regions of the inner chamber of the housing partitioned by the fixed vanes.
ハウジングの内室の底面およびプラグには、それぞれロータ本体の端部が回転可能に挿入される貫通孔が形成されている。これらの貫通孔は、流体保持室の開口部に相当する。ロータ本体の一方の端部がハウジングの内室の底面に形成された貫通孔に挿入され、かつロータ本体の他方の端部がプラグに形成された貫通孔に挿入されることにより、ロータは、ハウジングの内室に、この内室に対して相対的に回転可能に収容される。
The bottom of the inner chamber of the housing and the plug are respectively formed with through holes into which the end of the rotor body is rotatably inserted. These through holes correspond to the openings of the fluid holding chamber. The rotor is inserted by inserting one end of the rotor body into a through hole formed in the bottom of the inner chamber of the housing and inserting the other end of the rotor body into a through hole formed in the plug, The inner chamber of the housing is rotatably accommodated relative to the inner chamber.
以上のような構成において、ロータリダンパは、ロータに回転力が加えられて、ロータがハウジングの内室に対して相対的に回転すると、内室の固定ベーンに対してロータ回転方向の上流側に位置する領域が可動ベーンにより圧縮され、この領域の粘性流体に対する圧力が高まる。このため、この領域の粘性流体が、固定ベーンに形成された流路を介して、内室の固定ベーンに対してロータ回転方向の下流側に位置する領域へ移動する。この際、粘性流体の移動抵抗(流路を介した粘性流体の移動の困難性)に応じた制動トルクが発生する。
In the above configuration, when a rotational force is applied to the rotor and the rotor rotates relative to the inner chamber of the housing, the rotary damper is located upstream of the fixed vanes of the inner chamber in the rotor rotational direction. The area located is compressed by the movable vanes and the pressure on the viscous fluid in this area is increased. For this reason, the viscous fluid in this region moves to the region located on the downstream side in the rotor rotational direction with respect to the stationary vanes of the inner chamber via the flow path formed in the stationary vanes. At this time, a braking torque is generated according to the movement resistance of the viscous fluid (the difficulty of moving the viscous fluid through the flow path).
一般に、粘性流体の移動を制限することにより、外力に対して制動力を付与するダンパにおいて、流体保持室の開口部とこの開口部に挿入された抵抗力発生部材との間には、流体保持室に保持された粘性流体がこの隙間から漏れるのを防止するために、ゴム等の弾性体からなるOリングが配置されている。このため、つぎの問題が生じる。
Generally, in a damper that applies a damping force to an external force by restricting the movement of a viscous fluid, fluid retention is performed between the opening of the fluid holding chamber and the resistance generating member inserted into the opening. In order to prevent the viscous fluid held in the chamber from leaking from the gap, an O-ring made of an elastic material such as rubber is disposed. This causes the following problems.
すなわち、抵抗力発生部材に加ええられた外力によりOリングが弾性変形して、抵抗力発生部材の中心線が流体保持室の中心線から偏心し、軸ずれを引き起こす可能性がある。この軸ずれを抑制するためには、Oリングの剛性を高くする必要がある。しかし、Oリングの剛性を高くすると、抵抗力発生部材の移動あるいは回転に追従してOリングが弾性変形できずに、抵抗力発生部材とOリングとの隙間が生じ、流体保持室に保持された粘性流体がこの隙間から外部に漏れる可能性がある。
That is, the O-ring may be elastically deformed by the external force applied to the resistance generating member, and the center line of the resistance generating member may be eccentric from the center line of the fluid holding chamber to cause an axial deviation. In order to suppress this misalignment, it is necessary to increase the rigidity of the O-ring. However, if the rigidity of the O ring is increased, the O ring can not elastically deform following movement or rotation of the resistance generating member, and a gap between the resistance generating member and the O ring is generated, and the O ring is held in the fluid holding chamber. The viscous fluid may leak from this gap to the outside.
加えて、Oリングは、断面円形状であるため、径方向に弾性変形すると、抵抗力発生部材および流体保持室の開口部各々との接触面積が変化する。このため、抵抗力発生部材と流体保持室の開口部との間のシール性が不安定となり、流体保持室に保持された粘性流体がこの隙間から外部に漏れる可能性がさらに高まる。
In addition, since the O-ring is circular in cross section, elastic deformation in the radial direction changes the contact area with each of the resistance generating member and the opening of the fluid holding chamber. For this reason, the sealability between the resistance generating member and the opening of the fluid holding chamber becomes unstable, and the possibility of the viscous fluid held in the fluid holding chamber leaking to the outside from this gap further increases.
本発明は上記事情に鑑みてなされたものであり、その目的は、流体保持室に保持された粘性流体の漏れをより確実に防止することができるダンパを提供することにある。
The present invention has been made in view of the above circumstances, and an object thereof is to provide a damper capable of more reliably preventing the leakage of the viscous fluid held in the fluid holding chamber.
上記課題を解決するために、本発明のダンパでは、流体保持室の開口部にブッシュを装着して、このブッシュに抵抗力発生部材を摺動可能に保持させるとともに、このブッシュに保持された抵抗力発生部材と流体保持室の開口部との間に、流体保持室の中心線方向に幅を有し、流体保持室に圧接する外周面と、流体保持室の中心線方向に幅を有し、抵抗力発生部材に圧接する内周面と、を備える円環状の弾性部材を配置している。
In order to solve the above problems, in the damper according to the present invention, a bush is attached to the opening of the fluid holding chamber, and the bush is held slidably by the bush, and the resistance held by the bush Between the force generating member and the opening of the fluid holding chamber, it has a width in the direction of the center line of the fluid holding chamber, and has an outer peripheral surface pressed against the fluid holding chamber and a width in the direction of the center line of the fluid holding chamber And a ring-like elastic member including an inner circumferential surface pressed against the resistance generating member.
例えば、本発明は、
粘性流体の移動を制限することにより、外力に対して制動力を発生させるダンパであって、
開口部を有し、前記粘性流体を保持する流体保持室と、
前記流体保持室の前記開口部に挿入され、前記外力により前記流体保持室に対して相対的に移動する抵抗力発生部材と、
前記流体保持室内を仕切るとともに、前記流体保持室に対する前記抵抗力発生部材の相対的な移動に伴い、仕切られた前記流体保持室内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段と、
前記容量変更手段によって仕切られた前記流体保持室内の領域間を連結する流路と、
前記流体保持室の前記開口部に装着され、前記流体保持室の前記開口部に挿入された前記抵抗力発生部材を摺動可能に保持するブッシュと、
前記ブッシュに保持された前記抵抗力発生部材と前記流体保持室の前記開口部との間に配置された円環状の弾性部材と、を備え、
前記弾性部材は、
前記流体保持室の中心線方向に幅を有し、前記抵抗力発生部材に圧接する内周面と、
前記流体保持室の中心線方向に幅を有し、前記流体保持室に圧接する外周面と、を備えている。 For example, the present invention
A damper that generates a braking force against an external force by restricting the movement of a viscous fluid,
A fluid holding chamber having an opening and holding the viscous fluid;
A resistance generating member inserted into the opening of the fluid holding chamber and moved relative to the fluid holding chamber by the external force;
A capacity change which partitions the fluid holding chamber and compresses one region in the partitioned fluid holding chamber and extends the other region with relative movement of the resistance generating member with respect to the fluid holding chamber Means,
A flow path connecting between the regions in the fluid holding chamber partitioned by the volume changing means;
A bush attached to the opening of the fluid holding chamber and slidably holding the resistance generating member inserted into the opening of the fluid holding chamber;
And an annular elastic member disposed between the resistance generating member held by the bush and the opening of the fluid holding chamber.
The elastic member is
An inner circumferential surface having a width in a direction of a center line of the fluid holding chamber and in pressure contact with the resistance generating member;
And an outer peripheral surface which has a width in a direction of a center line of the fluid holding chamber and is in pressure contact with the fluid holding chamber.
粘性流体の移動を制限することにより、外力に対して制動力を発生させるダンパであって、
開口部を有し、前記粘性流体を保持する流体保持室と、
前記流体保持室の前記開口部に挿入され、前記外力により前記流体保持室に対して相対的に移動する抵抗力発生部材と、
前記流体保持室内を仕切るとともに、前記流体保持室に対する前記抵抗力発生部材の相対的な移動に伴い、仕切られた前記流体保持室内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段と、
前記容量変更手段によって仕切られた前記流体保持室内の領域間を連結する流路と、
前記流体保持室の前記開口部に装着され、前記流体保持室の前記開口部に挿入された前記抵抗力発生部材を摺動可能に保持するブッシュと、
前記ブッシュに保持された前記抵抗力発生部材と前記流体保持室の前記開口部との間に配置された円環状の弾性部材と、を備え、
前記弾性部材は、
前記流体保持室の中心線方向に幅を有し、前記抵抗力発生部材に圧接する内周面と、
前記流体保持室の中心線方向に幅を有し、前記流体保持室に圧接する外周面と、を備えている。 For example, the present invention
A damper that generates a braking force against an external force by restricting the movement of a viscous fluid,
A fluid holding chamber having an opening and holding the viscous fluid;
A resistance generating member inserted into the opening of the fluid holding chamber and moved relative to the fluid holding chamber by the external force;
A capacity change which partitions the fluid holding chamber and compresses one region in the partitioned fluid holding chamber and extends the other region with relative movement of the resistance generating member with respect to the fluid holding chamber Means,
A flow path connecting between the regions in the fluid holding chamber partitioned by the volume changing means;
A bush attached to the opening of the fluid holding chamber and slidably holding the resistance generating member inserted into the opening of the fluid holding chamber;
And an annular elastic member disposed between the resistance generating member held by the bush and the opening of the fluid holding chamber.
The elastic member is
An inner circumferential surface having a width in a direction of a center line of the fluid holding chamber and in pressure contact with the resistance generating member;
And an outer peripheral surface which has a width in a direction of a center line of the fluid holding chamber and is in pressure contact with the fluid holding chamber.
本発明では、流体保持室の開口部に装着されたブッシュにより抵抗力発生部材を摺動可能に保持するので、弾性部材の剛性を高くしなくても、抵抗力発生部材の軸ずれを抑制することができる。このため、抵抗力発生部材の移動あるいは回転に追従して弾性変形するように弾性部材の剛性を低くすることができ、これにより、抵抗力発生部材と弾性部材との隙間をなくして、流体保持室に保持された粘性流体が外部へ漏れる可能性を低減することができる。
In the present invention, since the resistance force generation member is slidably held by the bush attached to the opening of the fluid holding chamber, axial displacement of the resistance force generation member is suppressed without increasing the rigidity of the elastic member. be able to. For this reason, the rigidity of the elastic member can be lowered so as to elastically deform following the movement or rotation of the resistance generation member, thereby eliminating the gap between the resistance generation member and the elastic member, and holding the fluid The possibility of the viscous fluid held in the chamber leaking to the outside can be reduced.
さらに、本発明では、ブッシュに保持された抵抗力発生部材と流体保持室の開口部との間に、流体保持室の中心線方向に幅を有する内周面および外周面を備えた円環状の弾性部材を配置している。このため、抵抗力発生部材が軸ずれを起こして、弾性部材が径方向に弾性変形した場合でも、抵抗力発生部材および流体保持室の開口部各々と弾性部材との接触面積の変化を小さくすることができる。これにより、流体保持室の開口部と抵抗力発生材との間のシール性が安定し、流体保持室に保持された粘性流体が外部へ漏れる可能性をさらに低減することができる。
Further, according to the present invention, an annular shape having an inner peripheral surface and an outer peripheral surface having a width in the direction of the center line of the fluid holding chamber between the resistance generating member held by the bush and the opening of the fluid holding chamber. An elastic member is disposed. For this reason, even when the resistance generating member is axially displaced and the elastic member is elastically deformed in the radial direction, the change in the contact area between each of the openings of the resistance generating member and the fluid holding chamber and the elastic member is reduced. be able to. As a result, the sealability between the opening of the fluid holding chamber and the resistance generating material is stabilized, and the possibility of the viscous fluid held in the fluid holding chamber leaking to the outside can be further reduced.
以下、図面を参照して本発明の一実施の形態を説明する。
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
図1(A)~図1(C)は、本発明の一実施の形態に係るロータリダンパ1の正面図、側面図、および背面図である。また、図2(A)は、図1(A)に示すロータリダンパ1のA-A断面図であり、図2(B)は、図1(B)に示すロータリダンパ1のB-B断面図である。また、図3(A)および図3(B)は、図2(A)に示すロータリダンパ1のA部拡大図およびB部拡大図であり、図4(A)は、図2(A)に示すロータリダンパ1のC部拡大図であり、図4(B)は、図2(B)に示すロータリダンパ1のD部拡大図である。
FIGS. 1A to 1C are a front view, a side view, and a rear view of a rotary damper 1 according to an embodiment of the present invention. 2 (A) is a cross-sectional view of the rotary damper 1 taken along the line AA of FIG. 1 (A), and FIG. 2 (B) is a cross-sectional view of the rotary damper 1 shown in FIG. 1 (B). FIG. 3 (A) and 3 (B) are an enlarged view of a portion A and an enlarged view of a portion B of the rotary damper 1 shown in FIG. 2 (A), and FIG. 4 (A) is a sectional view of FIG. FIG. 4 (B) is an enlarged view of a portion D of the rotary damper 1 shown in FIG. 2 (B).
本実施の形態に係るロータリダンパ1は、自動車、鉄道車両、航空機、船舶等で用いられるリクライニング機能付きの座席シート等、双方向に回転する回転体の回転運動を制動することが必要とされる装置に利用される。図示するように、本実施の形態に係るロータリダンパ1は、オイル、シリコーン等の粘性流体(不図示)を保持する流体保持室を構成するケース2および蓋6と、流体保持室に対して相対的に回転可能に流体保持室に収容されたロータ3と、を備えている。
The rotary damper 1 according to the present embodiment is required to brake the rotational movement of a rotating body rotating in both directions, such as a seat with a reclining function used in automobiles, railway vehicles, aircraft, ships and the like. Used for the device. As shown, the rotary damper 1 according to the present embodiment is relative to the case 2 and the lid 6, which constitute a fluid holding chamber for holding a viscous fluid (not shown) such as oil or silicone, and the fluid holding chamber. And a rotor 3 rotatably accommodated in the fluid holding chamber.
図5(A)は、ケース2の正面図であり、図5(B)は、図5(A)に示すケース2のC-C断面図であり、図5(C)は、ケース2の背面図である。
5 (A) is a front view of the case 2, FIG. 5 (B) is a cross-sectional view of the case 2 shown in FIG. 5 (A) taken along the line CC, and FIG. It is a rear view.
図示するように、ケース2内には、一端が開口した円筒室(底付き円筒状の空間)21が形成されており、この円筒室21の底部22には、流体保持室の開口部として機能するロータ3挿入用の貫通孔23が形成されている。この貫通孔23には、後述の第一シールリング8aおよび第一ブッシュ4a(図4(A)参照)が装着され、ロータ3は、後述するロータ本体31の下端部33a(図6参照)がこの第一シールリング8aおよび第一ブッシュ4aが装着された貫通孔23に挿入されることにより、ロータ3の回転軸30が円筒室21の中心線20と一致するように、円筒室21内に収容される(図2(A)および図4(A)参照)。また、円筒室21の貫通孔23の内周面220には、第一シールリング8aおよび第一ブッシュ4aの軸方向外方(ロータリダンパ1の軸方向において、ケース2の外側に向かう方向)への移動をそれぞれ規制する段差221および段差222が形成されている。
As shown, a cylindrical chamber (a cylindrical space with a bottom) 21 with one end opened is formed in the case 2, and the bottom 22 of this cylindrical chamber 21 functions as an opening of a fluid holding chamber. A through hole 23 for inserting the rotor 3 is formed. A first seal ring 8a and a first bush 4a (see FIG. 4A) described later are attached to the through hole 23, and the rotor 3 has a lower end 33a (see FIG. 6) of a rotor main body 31 described later. By inserting the first seal ring 8 a and the first bush 4 a into the through hole 23, the rotary shaft 30 of the rotor 3 is aligned with the center line 20 of the cylindrical chamber 21. It is accommodated (see FIG. 2A and FIG. 4A). Further, on the inner circumferential surface 220 of the through hole 23 of the cylindrical chamber 21, the first seal ring 8 a and the first bush 4 a are axially outward (in the axial direction of the rotary damper 1, in the direction toward the outside of the case 2) A step 221 and a step 222 are formed which respectively restrict the movement of
また、円筒室21の内周面24には、径方向内方に突出し、先端面26がロータ3の後述するロータ本体31の外周面34(図6参照)と近接して、円筒室21を仕切る一対の仕切り部25が、円筒室21の中心線20に沿って、この中心線20に対して軸対称に形成されている。また、円筒室21の内周面24の開口側28には、蓋6の後述する雄ネジ部62(図9参照)と螺合する雌ネジ部27が形成されている。
Further, on the inner peripheral surface 24 of the cylindrical chamber 21, the cylindrical chamber 21 is projected with the tip end surface 26 in close proximity to the outer peripheral surface 34 (see FIG. 6) of the rotor main body 31 described later of the rotor 3. A pair of partitioning portions 25 that partition is formed axially symmetrical with respect to the center line 20 along the center line 20 of the cylindrical chamber 21. Further, on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21, a female screw portion 27 to be screwed with a male screw portion 62 (see FIG. 9) of the lid 6 described later is formed.
図6(A)および図6(B)は、ロータ3の正面図および側面図であり、図6(C)は、図6(A)に示すロータ3のD-D断面図である。
6 (A) and 6 (B) are a front view and a side view of the rotor 3, and FIG. 6 (C) is a DD cross-sectional view of the rotor 3 shown in FIG. 6 (A).
図示するように、ロータ3は、円筒状のロータ本体31と、ロータ本体31の回転軸30に対して軸対称に形成された一対のベーン(回転翼)32と、を備えている。
As illustrated, the rotor 3 includes a cylindrical rotor main body 31 and a pair of vanes (rotary blades) 32 formed in axial symmetry with respect to the rotation axis 30 of the rotor main body 31.
ベーン32は、ロータ3の回転軸30に沿って形成され、ロータ本体31の外周面34から径方向外方へ突出し、先端面35がケース2の円筒室21の内周面24と近接して、円筒室21を仕切る。ベーン32は、ケース2の円筒室21の仕切り部25とともに、ベーン32によって仕切られた流体保持室内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段を構成する。
The vanes 32 are formed along the rotation shaft 30 of the rotor 3 and project radially outward from the outer peripheral surface 34 of the rotor main body 31, and the tip end surface 35 approaches the inner peripheral surface 24 of the cylindrical chamber 21 of the case 2. , The cylindrical chamber 21 is divided. The vanes 32 together with the partition 25 of the cylindrical chamber 21 of the case 2 constitute capacity changing means for compressing one region in the fluid holding chamber partitioned by the vanes 32 and extending the other region.
ベーン32には、ロータ3の回転方向に沿ってベーン32の両側面37a、37b間を貫く流路36が形成されている。また、ベーン32には、バルブシール5が装着される(図2(B)および図4(B)参照)。
The vane 32 is formed with a flow passage 36 passing between the side surfaces 37 a and 37 b of the vane 32 along the rotational direction of the rotor 3. Further, the valve seal 5 is attached to the vane 32 (see FIG. 2 (B) and FIG. 4 (B)).
ロータ本体31は、外部からの回転力により流体保持室に対して相対的に回転する抵抗力発生部材として機能する。ロータ本体31は、下端部33aがケース2の円筒室21の底部22に形成された貫通孔23に回転可能に挿入され(図2(A)および図4(A)参照)、上端部33bが蓋6の後述する貫通孔60(図9参照)に回転可能に挿入される(図2(A)、図3(A)および図3(B)参照)。
The rotor main body 31 functions as a resistance generating member that rotates relative to the fluid holding chamber by the rotational force from the outside. The lower end portion 33a of the rotor main body 31 is rotatably inserted into the through hole 23 formed in the bottom portion 22 of the cylindrical chamber 21 of the case 2 (see FIGS. 2A and 4A). The lid 6 is rotatably inserted into a through hole 60 (see FIG. 9) described later (see FIG. 2A, FIG. 3A and FIG. 3B).
ロータ本体31には、外部からの回転力をロータ3に伝達する2面取り加工されたシャフト(不図示)を挿入するための挿入穴38が、回転軸30を中心にして形成されている。ロータ本体31の下端部33aは、ケース2の円筒室21の貫通孔23に装着された後述の第一シールリング8aおよび第一ブッシュ4aに、回転可能に挿入される(図4(A)参照)。そして、ロータ本体31の下端部33aの外周面34には、第一シールリング8aおよび第一ブッシュ4aの軸方向内方(ロータリダンパ1の軸方向において、ケース2の内側に向かう方向)への移動を規制する段差340aが形成されている。一方、ロータ本体31の上端部33bは、後述する蓋6の貫通孔60に装着された第二シールリング8bおよび第二ブッシュ4bに、回転可能に挿入される(図3(A)および図3(B)参照)。そして、ロータ本体31の上端部33bの外周面34には、第二シールリング8bおよび第二ブッシュ4bの軸方向内方への移動を規制する段差340bが形成されている。
An insertion hole 38 for inserting a 2-chamfered shaft (not shown) for transmitting an external rotational force to the rotor 3 is formed in the rotor body 31 with the rotation shaft 30 as a center. The lower end portion 33a of the rotor main body 31 is rotatably inserted into a first seal ring 8a and a first bush 4a described later mounted in the through hole 23 of the cylindrical chamber 21 of the case 2 (see FIG. 4A). ). The outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 is axially inward of the first seal ring 8a and the first bush 4a (inward in the axial direction of the rotary damper 1). A step 340a is formed to restrict movement. On the other hand, the upper end portion 33b of the rotor main body 31 is rotatably inserted in a second seal ring 8b and a second bush 4b mounted in a through hole 60 of the lid 6 described later (FIGS. 3A and 3) (B)). A step 340b is formed on the outer peripheral surface 34 of the upper end portion 33b of the rotor body 31 to restrict the axial inward movement of the second seal ring 8b and the second bush 4b.
図7(A)および図7(B)は、第一、第二ブッシュ4a、4bの側面図および正面図であり、図7(C)は、図7(B)に示す第一、第二ブッシュ4a、4bのE-E断面図である。
FIGS. 7A and 7B are a side view and a front view of the first and second bushes 4a and 4b, and FIG. 7C shows the first and second bushes shown in FIG. 7B. FIG. 5 is a cross-sectional view of the bushes 4a and 4b taken along the line EE.
図示するように、第一ブッシュ4aおよび第二ブッシュ4bは、摺動性に優れた材料で形成された円筒状部材であり、第一ブッシュ4aにおいては、ロータ3のロータ本体31の下端部33aの外周面34と摺接する内周面40aと、ケース2の円筒室21の貫通孔23の内周面220と当接する外周面41aと、を有し、第二ブッシュ4bにおいては、ロータ3のロータ本体31の上端部33bの外周面34と摺接する内周面40bと、蓋6の貫通孔60の内周面64(図9(D)参照)と当接する外周面41bと、を有する。
As illustrated, the first bush 4a and the second bush 4b are cylindrical members formed of a material excellent in slidability, and in the first bush 4a, the lower end portion 33a of the rotor body 31 of the rotor 3 is provided. And the outer peripheral surface 41a in contact with the inner peripheral surface 220a of the through hole 23 of the cylindrical chamber 21 of the case 2 in the second bush 4b. It has an inner circumferential surface 40b in sliding contact with the outer circumferential surface 34 of the upper end 33b of the rotor main body 31, and an outer circumferential surface 41b in contact with the inner circumferential surface 64 (see FIG. 9D) of the through hole 60 of the lid 6.
第一ブッシュ4aおよび第二ブッシュ4bは、黄銅合金等の金属、または、PTFE(ポリテトラフルオロエチレン)、ポリアセタール樹脂、ポリエチレン樹脂、ポリアミド樹脂、ポリフェニレンサルファイド樹脂等の合成樹脂で形成される。あるいは、円筒状の鋼板、樹脂コンポジット等のバック材の内周面上に、摺動層が複数層形成された複層摺動部材で形成してもよい。例えば、円筒状の鋼板からなるバック材の内周面に、焼結金属層を形成し、さらにその上にPTFEを含む樹脂摺動層を形成した複層摺動部材を用いることができる。
The first bush 4a and the second bush 4b are formed of metal such as brass alloy or synthetic resin such as PTFE (polytetrafluoroethylene), polyacetal resin, polyethylene resin, polyamide resin, polyphenylene sulfide resin and the like. Alternatively, a multi-layer sliding member in which a plurality of sliding layers are formed may be formed on the inner circumferential surface of a back member such as a cylindrical steel plate or resin composite. For example, it is possible to use a multilayer sliding member in which a sintered metal layer is formed on the inner circumferential surface of a back member made of a cylindrical steel plate and a resin sliding layer containing PTFE is further formed thereon.
図8(A)および図8(B)は、バルブシール5の正面図および側面図であり、図8(C)は、図8(A)に示すバルブシール5のF-F断面図である。
8A and 8B are a front view and a side view of the valve seal 5, and FIG. 8C is a cross-sectional view of the valve seal 5 shown in FIG. .
図示するように、バルブシール5は、ロータ3のベーン32に装着可能なコの字形状を有しており、ベーン32の回転方向の幅t1(図6(A)参照)より長い幅t2を有する底部50と、底部50の一方の端部51に一体的に形成され、ベーン32に形成された流路36の径方向の幅t3(図6(B)参照)より長い幅t4を有する第一脚部53と、底部50の他方の端部52に一体的に形成され、ベーン32に形成された流路36の径方向の幅t3より短い幅t5を有する第二脚部54と、を有する。
As illustrated, the valve seal 5 has a U-shape that can be attached to the vane 32 of the rotor 3 and has a width t2 longer than the width t1 (see FIG. 6A) of the vane 32 in the rotational direction. A bottom portion 50, and one end 51 of the bottom portion 50 integrally formed, and having a width t4 longer than a radial width t3 (see FIG. 6B) of the flow path 36 formed in the vane 32 One leg 53 and a second leg 54 integrally formed at the other end 52 of the bottom 50 and having a width t5 shorter than the radial width t3 of the flow passage 36 formed in the vane 32; Have.
ベーン32に装着されたバルブシール5は、底部50がベーン32の先端面35とケース2の円筒室21の内周面24との間に介在することにより、これらの隙間を塞ぐ(図4(B)参照)。また、図2(B)に示すように、ロータ3がケース2の円筒室21に対して相対的に第一回転方向R1に回転すると、バルブシール5の第一脚部53がベーン32の一方の側面37aと当接して、ベーン32に形成された流路36を塞ぐ。一方、ロータ3がケース2の円筒室21に対して相対的に第一回転方向R1の逆回転方向である第二回転方向R2に回転すると、バルブシール5の第一脚部53がベーン32の一方の側面37aから離れ、第二脚部54がベーン32の他方の側面37bに当接して、ベーン32に形成された流路36を開放する(図4(B)参照)。
The valve seal 5 mounted on the vane 32 closes these gaps by the bottom 50 being interposed between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21 of the case 2 (FIG. B) see). Further, as shown in FIG. 2B, when the rotor 3 rotates in the first rotational direction R1 relative to the cylindrical chamber 21 of the case 2, the first leg 53 of the valve seal 5 is one of the vanes 32. Abuts against the side surface 37a of the vane 32 to block the flow passage 36 formed in the vane 32. On the other hand, when the rotor 3 is rotated relative to the cylindrical chamber 21 of the case 2 in the second rotation direction R2 which is the reverse rotation direction of the first rotation direction R1, the first leg 53 of the valve seal 5 Away from one side surface 37a, the second leg 54 abuts on the other side surface 37b of the vane 32, and the flow path 36 formed in the vane 32 is opened (see FIG. 4B).
なお、バルブシール5は、相対的に回転するケース2およびロータ3間に配置されるため、摺動性に優れた材料、例えばポリアミド樹脂等の合成樹脂を用いることが好ましい。
In addition, since the valve seal 5 is disposed between the case 2 and the rotor 3 which are relatively rotated, it is preferable to use a material excellent in slidability, for example, a synthetic resin such as a polyamide resin.
図9(A)~図9(C)は、蓋6の正面図、側面図、および背面図であり、図9(D)は、図9(A)に示す蓋6のG-G断面図である。
9A to 9C are a front view, a side view, and a rear view of the lid 6, and FIG. 9D is a GG cross-sectional view of the lid 6 shown in FIG. 9A. It is.
図示するように、蓋6には、ケース2の円筒室21の底部22に形成された貫通孔23と対向する位置に、流体保持室の開口部として機能するロータ3挿入用の貫通孔60が形成されている。この貫通孔60には、後述の第二シールリング8bおよび第二ブッシュ4b(図3(A)参照)が装着され、ロータ3は、ロータ本体31の上端部33bがこの第二シールリング8bおよび第二ブッシュ4bが装着された貫通孔60に挿入される。また、貫通孔60の内周面64には、第二シールリング8bおよび第二ブッシュ4bの軸方向外方への移動をそれぞれ規制する段差65および段差66が形成されている。
As shown, the lid 6 has a through hole 60 for inserting the rotor 3 which functions as an opening of the fluid holding chamber at a position facing the through hole 23 formed in the bottom 22 of the cylindrical chamber 21 of the case 2. It is formed. A second seal ring 8b and a second bush 4b (see FIG. 3A) described later are attached to the through hole 60, and the upper end 33b of the rotor main body 31 of the rotor 3 is the second seal ring 8b and The second bush 4b is inserted into the through hole 60 mounted. Further, the inner circumferential surface 64 of the through hole 60 is formed with a step 65 and a step 66 which respectively restrict the outward movement of the second seal ring 8 b and the second bush 4 b in the axial direction.
また、蓋6の外周面61には、円筒室21の内周面24の開口側28に形成された雌ネジ部27と螺合する雄ネジ部62が形成されており、さらに、その下面63側に、Oリング7を装着するための溝67が周方向に形成されている。Oリング7は、溝67に装着され、蓋6の外周面61と円筒室21の内周面24との間に介在して、蓋6の雄ネジ部62と円筒室21の雌ネジ部27との螺合部分から粘性流体が外部に漏れるのを防止する(図3(A)および図3(B)参照)。
Further, on the outer peripheral surface 61 of the lid 6, a male screw portion 62 to be screwed with the female screw portion 27 formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21 is formed. On the side, a groove 67 for mounting the O-ring 7 is formed in the circumferential direction. The O-ring 7 is mounted in the groove 67 and is interposed between the outer peripheral surface 61 of the lid 6 and the inner peripheral surface 24 of the cylindrical chamber 21, and the male screw 62 of the lid 6 and the female screw 27 of the cylindrical chamber 21. And prevent the viscous fluid from leaking out of the screwed portion (see FIGS. 3A and 3B).
図10(A)は、第一、第二シールリング8a、8bの正面図であり、図10(B)は、図10(A)に示す第一、第二シールリング8a、8bのH-H断面図であり、図10(C)は、図10(A)に示す第一、第二シールリング8a、8bのE部拡大図であり、図10(D)は、図10(B)に示す第一、第二シールリング8a、8bのF部拡大図である。
Fig. 10 (A) is a front view of the first and second seal rings 8a and 8b, and Fig. 10 (B) is a view of H- of the first and second seal rings 8a and 8b shown in Fig. 10 (A). 10 (C) is an enlarged view of a portion E of the first and second seal rings 8a and 8b shown in FIG. 10 (A), and FIG. 10 (B) is FIG. 10 (B). It is the F section enlarged view of the 1st, 2nd seal rings 8a and 8b shown to.
図示するように、第一シールリング8aおよび第二シールリング8bは、ニトリルブタジエンゴム(NBR)等の弾性体で形成された円環状部材であり、第一シールリング8aにおいては、ロータ3のロータ本体31の下端部33aの外径d4より小さな内径d1と、ケース2の円筒室21の貫通孔23の内径(段差221の外径)d3より大きな外径d2と、を有し、第二シールリング8bにおいては、ロータ3のロータ本体31の上端部33bの外径d5より小さな内径d1と、蓋6の貫通孔60の内径(段差65の外径)d6より大きな外径d2と、を有する。また、第一シールリング8aおよび第二シールリング8bは、断面矩形状の内周側円環部81と、断面矩形状の外周側円環部82と、連結部83と、を有する。
As illustrated, the first seal ring 8a and the second seal ring 8b are annular members formed of an elastic body such as nitrile butadiene rubber (NBR), and in the first seal ring 8a, the rotor of the rotor 3 is The second seal has an inner diameter d1 smaller than the outer diameter d4 of the lower end portion 33a of the main body 31, and an outer diameter d2 larger than the inner diameter d3 of the through hole 23 of the cylindrical chamber 21 of the case 2 (the outer diameter of the step 221). The ring 8b has an inner diameter d1 smaller than the outer diameter d5 of the upper end 33b of the rotor body 31 of the rotor 3 and an outer diameter d2 larger than the inner diameter d5 of the through hole 60 of the lid 6 (the outer diameter of the step 65). . The first seal ring 8 a and the second seal ring 8 b have an inner circumferential side annular portion 81 having a rectangular cross section, an outer circumferential side annular portion 82 having a rectangular cross section, and a connecting portion 83.
内周側円環部81は、ケース2の円筒室21の中心線20と一致する中心線80の方向に平坦な幅t6の内周面84を有する。内周面84が中心線80の方向に平坦な幅t6を有することにより、第一シールリング8aおよび第二シールリング8bが径方向に弾性変形した場合における内周面84と相手面との接触面積の変化を抑制することができる。なお、内周面84は、第一シールリング8aにおいてはロータ3のロータ本体31の下端部33aの外周面34に圧接し、第二シールリング8bにおいてはロータ3のロータ本体31の上端部33bの外周面34に圧接する。また、内周面84には、グリース溝86が円周方向に形成されており、グリースがこのグリース溝86に充填される。なお、ここでは、円周方向のグリース溝86を内周面84に一つ形成しているが、円周方向のグリース溝86は内周面84に複数形成してもよい。
The inner circumferential side annular portion 81 has an inner circumferential surface 84 having a flat width t6 in the direction of the center line 80 coinciding with the center line 20 of the cylindrical chamber 21 of the case 2. When the inner peripheral surface 84 has a flat width t6 in the direction of the center line 80, the contact between the inner peripheral surface 84 and the mating surface when the first seal ring 8a and the second seal ring 8b are elastically deformed in the radial direction. A change in area can be suppressed. The inner peripheral surface 84 is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 of the rotor 3 in the first seal ring 8a, and the upper end 33b of the rotor main body 31 of the rotor 3 in the second seal ring 8b. The outer circumferential surface 34 of the Further, a grease groove 86 is formed in the circumferential direction on the inner circumferential surface 84, and the grease is filled in the grease groove 86. Although one grease groove 86 in the circumferential direction is formed in the inner circumferential surface 84 here, a plurality of grease grooves 86 in the circumferential direction may be formed in the inner circumferential surface 84.
外周側円環部82は、ケース2の円筒室21の中心線20と一致する中心線80の方向に平坦な幅t7の外周面85を有する。外周面85が中心線80の方向に平坦な幅t7を有することにより、第一シールリング8aおよび第二シールリング8bが径方向に弾性変形した場合における外周面85と相手面との接触面積の変化を抑制することができる。なお、外周面85は、第一シールリング8aにおいてはケース2の円筒室21の貫通孔23の内周面220に圧接し、第二シールリング8bにおいては蓋6の貫通孔60の内周面64に圧接する。
The outer circumferential side annular portion 82 has an outer circumferential surface 85 having a flat width t7 in the direction of the center line 80 which coincides with the center line 20 of the cylindrical chamber 21 of the case 2. Since the outer peripheral surface 85 has a flat width t7 in the direction of the center line 80, the contact area between the outer peripheral surface 85 and the mating surface when the first seal ring 8a and the second seal ring 8b are elastically deformed in the radial direction. Change can be suppressed. The outer circumferential surface 85 is in pressure contact with the inner circumferential surface 220 of the through hole 23 of the cylindrical chamber 21 of the case 2 in the first seal ring 8a, and the inner circumferential surface of the through hole 60 of the lid 6 in the second seal ring 8b. Press into contact with 64.
ここで、内周側円環部81の内周面84の幅t6は、外周側円環部82の外周面85の幅t7より狭い(t6<t7)。このため、内周側円環部81の内周面84の摩擦抵抗が外周側円環部82の外周面85の摩擦抵抗より小さくなる。したがって、ロータ3がケース2の円筒室21に対して相対的に回転した場合、摩擦係数の低い内周側円環部81の内周面84において、この内周面84が圧接するロータ3のロータ本体31の下端部33aあるいは上端部33bの外周面34との摺動が発生し、摩擦係数の高い外周側円環部82の外周面85においては、この外周面85が圧接するケース2の円筒室21の貫通孔23の内周面220あるいは蓋6の貫通孔60の内周面64と摺動せずに密着状態となる。
Here, the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81 is narrower than the width t7 of the outer circumferential surface 85 of the outer circumferential side annular portion 82 (t6 <t7). For this reason, the frictional resistance of the inner circumferential surface 84 of the inner circumferential side annular portion 81 becomes smaller than the frictional resistance of the outer circumferential surface 85 of the outer circumferential side annular portion 82. Therefore, when the rotor 3 is rotated relative to the cylindrical chamber 21 of the case 2, the inner peripheral surface 84 of the rotor 3 is in pressure contact with the inner peripheral surface 84 of the inner peripheral side annular portion 81 having a low coefficient of friction. Sliding with the outer peripheral surface 34 of the lower end portion 33a or the upper end 33b of the rotor main body 31 occurs, and the outer peripheral surface 85 of the outer peripheral side annular portion 82 having a high coefficient of friction It does not slide with the inner peripheral surface 220 of the through hole 23 of the cylindrical chamber 21 or the inner peripheral surface 64 of the through hole 60 of the lid 6, and a close contact state is established.
ただし、第一シールリング8aおよび第二シールリング8bのゴム硬度の範囲をショアA30~ショアD60とした場合、内周側円環部81の内周面84の幅t6は、外周側円環部82の外周面85の幅t7に対して、t7/t6≦3とすることが好ましい。t7/t6>3の場合、外周側円環部82の外周面85の幅t7が内周側円環部81の内周面84の幅t6に対して長くなりすぎて、外周側円環部82の外周面85の端部が径方向内方に撓んでしまい、所望のシール性能を得られない可能性がある。また、第一シールリング8aおよび第二シールリング8bの設置スペースが大きくなる。
However, when the range of the rubber hardness of the first seal ring 8a and the second seal ring 8b is Shore A30 to Shore D60, the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81 is the outer circumferential side annular portion It is preferable to set t7 / t6 ≦ 3 with respect to the width t7 of the outer peripheral surface 85 of 82. In the case of t7 / t6> 3, the width t7 of the outer circumferential surface 85 of the outer circumferential side annular portion 82 is too long relative to the width t6 of the inner circumferential surface 84 of the inner circumferential side annular portion 81, and the outer circumferential side annular portion The end portion of the outer peripheral surface 85 of 82 may be bent radially inward, and a desired sealing performance may not be obtained. Also, the installation space of the first seal ring 8a and the second seal ring 8b is increased.
また、第一シールリング8aおよび第二シールリング8bのゴム硬度の範囲をショアA30~ショアD60とした場合、内周側円環部81の内周面84に設けられたグリース溝86の幅(グリース溝86が内周面84に複数設けられている場合は、これらグリース溝86の幅の合計)t9は、内周側円環部81の内周面84の幅t6に対して、0.05≦t9/t6≦0.5であることが好ましい。t9/t6が0.05より小さくなると、グリース溝86における潤滑グリースの保持量が低下して摺動性能が低下する。一方、t9/t6が0.5より大きくなると、内周側円環部81の内周面84が圧接するロータ3のロータ本体31の下端部33aあるいは上端部33bの外周面34との接触面積が小さくなりすぎてシール性が低下する。
When the range of rubber hardness of the first seal ring 8 a and the second seal ring 8 b is Shore A 30 to Shore D 60, the width of the grease groove 86 provided on the inner circumferential surface 84 of the inner circumferential side annular portion 81 ( When a plurality of grease grooves 86 are provided on the inner circumferential surface 84, the sum of the widths of the grease grooves 86) is equal to 0. 0. with respect to the width t6 of the inner circumferential surface 84 of the inner circumferential annular portion 81. It is preferable that 05 ≦ t9 / t6 ≦ 0.5. When t9 / t6 is smaller than 0.05, the amount of retained lubricating grease in the grease groove 86 is reduced and sliding performance is reduced. On the other hand, when t9 / t6 becomes larger than 0.5, the contact area with the outer peripheral surface 34 of the lower end 33a or the upper end 33b of the rotor body 31 of the rotor 3 to which the inner peripheral surface 84 of the inner peripheral side annular part 81 is in pressure contact Becomes too small and the sealing performance is reduced.
連結部83は、内周側円環部81および外周側円環部82間に配されて、両者を連結する。また、連結部83は、中心線80の方向において、内周側円環部81の幅(内周面84の幅)t6および外周側円環部82の幅(外周面85の幅)t7よりも狭い幅t8を有している(t8<t6<t7)。このため、第一シールリング8aおよび第二シールリング8bに応力が加わった場合に、連結部83が弾性変形してこの応力を吸収することにより、内周側円環部81および外周側円環部82の弾性変形が抑制される。
The connecting portion 83 is disposed between the inner peripheral side annular ring portion 81 and the outer peripheral side annular portion 82 to connect the both. Further, in the direction of center line 80, connecting portion 83 has a width (width of inner circumferential surface 84) t6 of inner circumferential side annular portion 81 and a width (width of outer circumferential surface 85) t7 of outer circumferential side annular portion 82. Also has a narrow width t8 (t8 <t6 <t7). Therefore, when stress is applied to the first seal ring 8a and the second seal ring 8b, the connecting portion 83 is elastically deformed to absorb the stress, thereby the inner circumferential side annular portion 81 and the outer circumferential side annular ring Elastic deformation of the portion 82 is suppressed.
ここで、第一シールリング8aおよび第二シールリング8bのゴム硬度の範囲をショアA30~ショアD60とした場合、連結部83の幅t8は、内周側円環部81の幅t6に対して、0.3≦t8/t6≦0.95とすることが好ましい。t8/t6が0.3より小さいと、連結部83の剛性が低下し、内周側円環部81の内周面84のロータ3のロータ本体31の下端部33aあるいは上端部33bの外周面34に対する押圧力が弱くなりすぎて、シール性が低下する。一方、t8/t6が0.95より大きいと、連結部83の剛性が高くなり、内周側円環部81の内周面84のロータ3のロータ本体31の下端部33aあるいは上端部33bの外周面34に対する押圧力が強くなりすぎて、摺動性能が低下する。
Here, when the range of the rubber hardness of the first seal ring 8 a and the second seal ring 8 b is set to Shore A 30 to Shore D 60, the width t 8 of the connecting portion 83 is relative to the width t 6 of the inner circumferential annular portion 81 Preferably, 0.3 ≦ t8 / t6 ≦ 0.95. When t8 / t6 is smaller than 0.3, the rigidity of the connecting portion 83 is reduced, and the outer peripheral surface of the lower end portion 33a or the upper end portion 33b of the rotor body 31 of the rotor 3 of the inner peripheral surface 84 of the inner peripheral side annular portion 81 The pressing force against 34 becomes too weak and the sealing performance is reduced. On the other hand, when t8 / t6 is larger than 0.95, the rigidity of the connecting portion 83 becomes high, and the lower end portion 33a or the upper end portion 33b of the rotor main body 31 of the rotor 3 of the inner peripheral surface 84 of the inner peripheral side annular portion 81 The pressing force against the outer peripheral surface 34 becomes too strong, and the sliding performance is reduced.
上記構成のロータリダンパ1において、ロータ3がケース2の円筒室21に対して相対的に第一回転方向R1に回転移動すると(図2(B)参照)、ロータ3のベーン32に装着されたバルブシール5の第一脚部53がベーン32の一方の側面37aと当接して、ベーン32に形成された流路36を塞ぐ。このとき、バルブシール5により、ベーン32の先端面35とケース2の円筒室21の内周面24との隙間が塞がれている(図4(B)参照)。したがって、円筒室21内に充填された粘性流体の移動が、ケース2の円筒室21の仕切り部25の先端面26とロータ3のロータ本体31の外周面34との隙間g1、仕切り部25の上面29と蓋6の下面63との隙間g2、および、蓋6の下面63とロータ3のベーン32の上面38との隙間g3等を介してのみに制限され(図3(A)および図3(B)参照)、ベーン32とベーン32に対して第一回転方向R1側に位置する仕切り部25とにより区切られた領域21a(図2(B)参照)内の粘性流体に対する圧力が高まる。このため、強い制動トルクが発生する。
In the rotary damper 1 configured as described above, when the rotor 3 is rotationally moved relative to the cylindrical chamber 21 of the case 2 in the first rotational direction R1 (see FIG. 2B), the vanes 32 of the rotor 3 are mounted. The first leg 53 of the valve seal 5 abuts on one side surface 37 a of the vane 32 to close the flow passage 36 formed in the vane 32. At this time, the gap between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21 of the case 2 is closed by the valve seal 5 (see FIG. 4B). Therefore, the movement of the viscous fluid filled in the cylindrical chamber 21 is determined by the gap g1 between the tip surface 26 of the partition 25 of the cylindrical chamber 21 of the case 2 and the outer peripheral surface 34 of the rotor main body 31 of the rotor 3. The gap g2 between the upper surface 29 and the lower surface 63 of the lid 6 and the gap g3 between the lower surface 63 of the lid 6 and the upper surface 38 of the vane 32 of the rotor 3 are limited only (Figs. 3A and 3). (See (B)) The pressure on the viscous fluid in the area 21a (see FIG. 2B) divided by the vane 32 and the partition 25 positioned on the first rotational direction R1 side with respect to the vane 32 is increased. For this reason, a strong braking torque is generated.
一方、ロータ3がケース2の円筒室21に対して相対的に第二回転方向R2に回転移動すると(図2(B)参照)、ロータ3のベーン32に装着されたバルブシール5の第一脚部53がベーン32の一方の側面37aから離れて、ベーン32に形成された流路36を開放する。したがって、円筒室21内に充填された粘性流体の移動が、上述の隙間g1~g3等に加えて、ベーン32に形成された流路36を介して行われるため、ベーン32とベーン32に対して第二回転方向R2側に位置する仕切り部25とにより区切られた領域21b(図2(B)参照)内の粘性流体に対する圧力は、ロータ3がケース2の円筒室21に対して相対的に第一回転方向R1に回転した場合に比べて高くならない。このため、ロータ3がケース2の円筒室21に対して相対的に第一回転方向R1に回転した場合よりも弱い制動トルクが発生する。
On the other hand, when the rotor 3 is rotationally moved relative to the cylindrical chamber 21 of the case 2 in the second rotational direction R2 (see FIG. 2B), the first valve seal 5 mounted on the vane 32 of the rotor 3 The leg 53 separates from one side 37 a of the vane 32 to open the flow passage 36 formed in the vane 32. Therefore, the movement of the viscous fluid filled in the cylindrical chamber 21 is performed through the flow path 36 formed in the vane 32 in addition to the gaps g1 to g3 and the like described above. The pressure with respect to the viscous fluid in the area 21b (see FIG. 2B) divided by the partition 25 positioned on the second rotational direction R2 side is the relative pressure of the rotor 3 to the cylindrical chamber 21 of the case 2 It is not higher than the case of rotating in the first rotation direction R1. Therefore, a braking torque that is weaker than when the rotor 3 rotates in the first rotational direction R1 relative to the cylindrical chamber 21 of the case 2 is generated.
以上、本発明の一実施の形態を説明した。
Hereinabove, one embodiment of the present invention has been described.
本実施の形態では、ケース2の円筒室21の貫通孔23および蓋6の貫通孔60のそれぞれに装着された第一ブッシュ4aおよび第二ブッシュ4bによりロータ3を摺動可能に保持しているので、第一ブッシュ4aおよび第二ブッシュ4bとともにロータ3を摺動可能に保持する第一シールリング8aおよび第二シールリング8bの剛性を高くしなくても、ロータ3の軸ずれを抑制することができる。このため、ロータ3の回転に追従して弾性変形するように第一シールリング8aおよび第二シールリング8bの剛性を低くすることができ、これにより、ロータ3と第一シールリング8aおよび第二シールリング8bとの隙間をなくして、ケース2の円筒室21に保持された粘性流体が外部へ漏れる可能性を低減することができる。
In the present embodiment, the rotor 3 is slidably held by the first bush 4 a and the second bush 4 b attached to the through hole 23 of the cylindrical chamber 21 of the case 2 and the through hole 60 of the lid 6 respectively. Therefore, the axial displacement of the rotor 3 can be suppressed without increasing the rigidity of the first seal ring 8a and the second seal ring 8b that slidably holds the rotor 3 together with the first bush 4a and the second bush 4b. Can. Therefore, the rigidity of the first seal ring 8a and the second seal ring 8b can be lowered so as to elastically deform following the rotation of the rotor 3, whereby the rotor 3 and the first seal ring 8a and the second By eliminating the gap with the seal ring 8b, the possibility of the viscous fluid held in the cylindrical chamber 21 of the case 2 leaking to the outside can be reduced.
また、本実施の形態では、ケース2の円筒室21の貫通孔23とロータ3のロータ本体31の下端部33aとの間に、円筒室21の中心線20の方向に平坦な幅t7を有し、貫通孔23の内周面220に圧接する外周面85と、円筒室21の中心線20の方向に平坦な幅t6を有し、ロータ本体31の下端部33aの外周面34に圧接する内周面84と、を備える弾性体の第一シールリング8aを配置するとともに、蓋6の貫通孔60とロータ本体31の上端部33bとの間に、円筒室21の中心線20の方向に平坦な幅t7を有し、貫通孔60の内周面64に圧接する外周面85と、円筒室21の中心線20の方向に平坦な幅t6を有し、ロータ本体31の上端部33bの外周面34に圧接する内周面84と、を備える弾性体の第二シールリング8bを配置している。
Further, in the present embodiment, between the through-hole 23 of the cylindrical chamber 21 of the case 2 and the lower end 33a of the rotor main body 31 of the rotor 3, the flat width t7 in the direction of the center line 20 of the cylindrical chamber 21 is provided. And has a flat width t6 in the direction of the center line 20 of the cylindrical chamber 21 and is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor body 31. In the direction of the center line 20 of the cylindrical chamber 21 between the through hole 60 of the lid 6 and the upper end 33b of the rotor main body 31 while arranging the first seal ring 8a of the elastic body provided with the inner circumferential surface 84; An outer peripheral surface 85 having a flat width t7 and in pressure contact with the inner peripheral surface 64 of the through hole 60 and a flat width t6 in the direction of the center line 20 of the cylindrical chamber 21 An inner circumferential surface 84 in pressure contact with the outer circumferential surface 34; It is arranged ring 8b.
このため、第一、第二シールリング8a、8bの代わりに断面円形状のOリングを用いた場合に比べて、ロータ3が軸ずれを起こして、第一、第二シールリング8a、8bが径方向に弾性変形した場合における、第一シールリング8aとロータ本体31の下端部33aとの接触面積、第一シールリング8aと円筒室21の貫通孔23との接触面積、第二シールリング8bとロータ本体31の上端部33bとの接触面積、および第二シールリング8bと蓋6の貫通孔60との接触面積の変化を抑制することができる。これにより、円筒室21の貫通孔23とロータ本体31の下端部33aとの間、および、蓋6の貫通孔60とロータ本体31の上端部33bとの間のシール性が安定して、円筒室21内に充填された粘性流体がこれらの隙間から漏れる可能性をさらに低減することができる。
Therefore, as compared with the case where the O-ring having a circular cross section is used instead of the first and second seal rings 8a and 8b, the rotor 3 is axially offset and the first and second seal rings 8a and 8b are The contact area between the first seal ring 8a and the lower end portion 33a of the rotor body 31, the contact area between the first seal ring 8a and the through hole 23 of the cylindrical chamber 21, and the second seal ring 8b when elastically deformed in the radial direction. It is possible to suppress changes in the contact area between the upper end portion 33b of the rotor main body 31 and the contact area between the second seal ring 8b and the through hole 60 of the lid 6. Thereby, the sealing performance between the through hole 23 of the cylindrical chamber 21 and the lower end 33a of the rotor main body 31 and between the through hole 60 of the lid 6 and the upper end 33b of the rotor main body 31 is stabilized. The possibility that the viscous fluid filled in the chamber 21 leaks from these gaps can be further reduced.
また、本実施の形態によれば、第一、第二シールリング8a、8bの内周面84の幅t6を外周面85の幅t7より狭くしている。このため、内周面84の摩擦抵抗が外周面85の摩擦抵抗より小さくなり、ロータ3がケース2の円筒室21に対して相対的に回転した場合、摩擦係数の小さい内周面84において相手面(第一シールリング8aではロータ本体31の下端部33aの外周面34が該当し、第二シールリング8bではロータ本体31の上端部33bの外周面34が該当する)との摺動が発生し、摩擦係数の高い外周面85は相手面(第一シールリング8aでは円筒室21の貫通孔23の内周面220が該当し、第二シールリング8bでは蓋6の貫通孔60の内周面64が該当する)と摺動せずに密着状態となる。したがって、周長の短い内周面84においてのみ、相手面との摺動が発生するため、第一シールリング8aおよび第二シールリング8bの摩耗量を減らして、寿命を延ばすことができる。
Further, according to the present embodiment, the width t6 of the inner peripheral surface 84 of the first and second seal rings 8a and 8b is smaller than the width t7 of the outer peripheral surface 85. For this reason, when the frictional resistance of the inner peripheral surface 84 becomes smaller than the frictional resistance of the outer peripheral surface 85 and the rotor 3 rotates relative to the cylindrical chamber 21 of the case 2, the other is The sliding occurs with the surface (in the first seal ring 8a, the outer peripheral surface 34 of the lower end 33a of the rotor main body 31 corresponds, and in the second seal ring 8b, the outer peripheral surface 34 of the upper end 33b of the rotor main body 31 corresponds) The outer peripheral surface 85 having a high coefficient of friction corresponds to the mating surface (in the first seal ring 8a, the inner peripheral surface 220 of the through hole 23 of the cylindrical chamber 21 corresponds, and in the second seal ring 8b the inner periphery of the through hole 60 of the lid 6 It comes in close contact without sliding with the surface 64). Therefore, since the sliding with the opposite surface occurs only on the inner circumferential surface 84 with a short circumferential length, the wear amount of the first seal ring 8a and the second seal ring 8b can be reduced and the life can be extended.
また、本実施の形態によれば、第一、第二シールリング8a、8bの内周面84にグリース溝86を円周方向に形成して、このグリース溝86にグリースを充填している。このため、第一、第二シールリング8a、8bとロータ3との摩擦抵抗を小さくして、ロータ3をより滑らかに摺動させることができる。
Further, according to the present embodiment, the grease groove 86 is formed in the circumferential direction on the inner peripheral surface 84 of the first and second seal rings 8a and 8b, and the grease groove 86 is filled with the grease. For this reason, it is possible to make the rotor 3 slide more smoothly by reducing the frictional resistance between the first and second seal rings 8a and 8b and the rotor 3.
また、本実施の形態において、第一、第二シールリング8a、8bは、内周面84を含む断面矩形状の内周側円環部81と、外周面85を含む断面矩形状の外周側円環部82と、内周側円環部81と外周側円環部82とを連結する連結部83と、を備えており、連結部83は、円筒室21の中心線20の方向において、内周側円環部81および外周側円環部82より狭い幅t8を有している。このため、第一、第二シールリング8a、8bに応力が加わった場合に、連結部82が弾性変形してこの応力を吸収することにより、内周側円環部81および外周側円環部82の弾性変形が抑制され、第一シールリング8aとロータ本体31の下端部33aとの接触面積、第一シールリング8aと円筒室21の貫通孔23との接触面積、第二シールリング8bとロータ本体31の上端部33bとの接触面積、および、第二シールリング8bと蓋6の貫通孔60との接触面積の変化をさらに抑制することができる。したがって、円筒室21の貫通孔23とロータ本体31の下端部33aとの間、および、蓋6の貫通孔60とロータ本体31の上端部33bとの間のシール性がさらに安定して、円筒室21内に充填された粘性流体がこれらの隙間から漏れる可能性をさらに低減することができる。
Further, in the present embodiment, the first and second seal rings 8 a and 8 b have an outer circumferential side having a rectangular cross section including an inner circumferential surface 84 and an outer circumferential side having a rectangular cross section including an outer circumferential surface 85. An annular portion 82 and a connecting portion 83 for connecting the inner circumferential side annular portion 81 and the outer circumferential side annular portion 82 are provided. The connecting portion 83 is in the direction of the center line 20 of the cylindrical chamber 21. It has a width t8 narrower than the inner circumferential side annular portion 81 and the outer circumferential side annular portion 82. For this reason, when stress is applied to the first and second seal rings 8a and 8b, the connecting portion 82 is elastically deformed to absorb the stress, thereby the inner circumferential side annular portion 81 and the outer circumferential side annular portion The elastic deformation of the first seal ring 8a and the lower end portion 33a of the rotor main body 31 is suppressed, the contact area of the first seal ring 8a and the through hole 23 of the cylindrical chamber 21 and the second seal ring 8b. It is possible to further suppress changes in the contact area with the upper end portion 33 b of the rotor main body 31 and the contact area between the second seal ring 8 b and the through hole 60 of the lid 6. Therefore, the sealing performance between the through hole 23 of the cylindrical chamber 21 and the lower end 33a of the rotor main body 31, and between the through hole 60 of the lid 6 and the upper end 33b of the rotor main body 31 is further stabilized. The possibility that the viscous fluid filled in the chamber 21 leaks from these gaps can be further reduced.
また、本実施の形態では、ケース2の円筒室21の貫通孔23の内周面220に、第一シールリング8aおよび第一ブッシュ4aの軸方向外方への移動をそれぞれ規制する段差221および段差222を形成するとともに、ロータ本体31の下端部33aの外周面34に、装着された第一シールリング8aおよび第一ブッシュ4aの軸方向内方への移動を規制する段差340aを形成している。これにより、第一シールリング8aおよび第一ブッシュ4aの軸方向への移動が規制され、第一シールリング8aによるシール性を向上させることができるとともに、第一ブッシュ4aによるロータ3の保持位置が安定してロータ3の軸ずれをより効果的に抑制することができる。
Further, in the present embodiment, on the inner circumferential surface 220 of the through hole 23 of the cylindrical chamber 21 of the case 2, the step 221 and the outward movement of the first seal ring 8a and the first bush 4a are restricted. A step 222 is formed, and a step 340a is formed on the outer peripheral surface 34 of the lower end portion 33a of the rotor main body 31 to restrict the axially inward movement of the attached first seal ring 8a and the first bush 4a. There is. Thereby, the axial movement of the first seal ring 8a and the first bush 4a is restricted, and the sealability by the first seal ring 8a can be improved, and the holding position of the rotor 3 by the first bush 4a is The axis offset of the rotor 3 can be stably suppressed more effectively.
同様に、本実施の形態では、蓋6の貫通孔60の内周面64に、第二シールリング8bおよび第二ブッシュ4bの軸方向外方への移動をそれぞれ規制する段差65および段差66を形成するとともに、ロータ本体31の上端部33bの外周面34に、第二シールリング8bおよび第二ブッシュ4bの軸方向内方への移動を規制する段差340bを形成している。これにより、第二シールリング8bおよび第二ブッシュ4bの軸方向への移動が規制され、第二シールリング8bによるシール性をより向上させることができるとともに、第二ブッシュ4bによるロータ3の保持位置が安定してロータ3の軸ずれをより効果的に抑制することができる。
Similarly, in the present embodiment, the inner circumferential surface 64 of the through hole 60 of the lid 6 is provided with a step 65 and a step 66 for restricting the outward movement of the second seal ring 8b and the second bush 4b in the axial direction. A step 340b is formed on the outer peripheral surface 34 of the upper end portion 33b of the rotor main body 31 to restrict the axial inward movement of the second seal ring 8b and the second bush 4b. Thereby, the axial movement of the second seal ring 8b and the second bush 4b is restricted, and the sealability by the second seal ring 8b can be further improved, and the holding position of the rotor 3 by the second bush 4b Thus, the axial displacement of the rotor 3 can be suppressed more effectively.
また、本実施の形態によれば、バルブシール5にポリアミド等の摺動性に優れた樹脂を用いることにより、バルブシール5がロータ3のロータ本体31の外周面34を摺動可能に支持する滑り軸受として機能するため、第一ブッシュ4aおよび第二ブッシュ4bとともに、外部からの回転力をロータ3に伝達するシャフトの偏心等によるガタつきを吸収して、シャフトを滑らかに回転させることができる。
Further, according to the present embodiment, the valve seal 5 slidably supports the outer peripheral surface 34 of the rotor main body 31 of the rotor 3 by using the resin having excellent slidability such as polyamide for the valve seal 5. Since it functions as a slide bearing, it is possible to smoothly rotate the shaft by absorbing rattling due to eccentricity or the like of the shaft that transmits the rotational force from the outside to the rotor 3 together with the first bush 4a and the second bush 4b. .
なお、本発明は、上記の実施の形態に限定されるものではなく、その要旨の範囲内で数々の変形が可能である。
The present invention is not limited to the above embodiment, and various modifications are possible within the scope of the invention.
例えば、上記の実施の形態では、第一ブッシュ4aを第一シールリング8aに対して軸方向外方に配置しているが(図2(A)および図4(A)参照)、第一ブッシュ4aを第一シールリング8aに対して軸方向内方に配置してもよい。同様に、上記の実施の形態では、第二ブッシュ4bを第二シールリング8bに対して軸方向外方に配置しているが(図2(A)、図3(A)および図3(B)参照)、第二ブッシュ4bを第二シールリング8bに対して軸方向内方に配置してもよい。これらの場合、ケース2の円筒室21に潤滑性の優れた粘性流体を保持させることにより、第一ブッシュ4aおよび第二ブッシュ4bをケース2の円筒室21に保持された粘性流体で潤滑することができるので、ロータ3をより滑らかに回転可能に保持することができる。
For example, in the above embodiment, the first bush 4a is disposed axially outward with respect to the first seal ring 8a (see FIGS. 2A and 4A). 4a may be disposed axially inward with respect to the first seal ring 8a. Similarly, in the above embodiment, the second bush 4b is disposed axially outward with respect to the second seal ring 8b (FIG. 2 (A), FIG. 3 (A) and FIG. 3 (B). ), The second bush 4b may be disposed axially inward with respect to the second seal ring 8b. In these cases, the first bush 4a and the second bush 4b are lubricated with the viscous fluid held in the cylindrical chamber 21 of the case 2 by holding the viscous fluid having excellent lubricity in the cylindrical chamber 21 of the case 2. As a result, the rotor 3 can be rotatably held more smoothly.
また、上記の実施の形態では、第一、第二シールリング8a、8bとして、内周面84を含む断面矩形状の内周側円環部81と、外周面85を含む断面矩形状の外周側円環部82と、内周側円環部81および外周側円環部82を連結する連結部83と、を有するものを用いているが、本発明はこれに限定されない。第一、第二シールリング8a、8bは、円筒室21の中心線20の方向に幅t6を有する内周面84と、円筒室21の中心線20の方向に幅t7を有する外周面85と、を備えているものであればよい。例えば、内周面84および外周面85を備えた断面矩形状の円環部材であってもよい。
In the above embodiment, as the first and second seal rings 8a and 8b, the outer peripheral side annular portion 81 having a rectangular cross section including the inner peripheral surface 84 and the outer periphery having a rectangular cross section including the outer peripheral surface 85 Although what has the side annular ring part 82, and the connection part 83 which connects the inner peripheral side annular ring part 81 and the outer peripheral side annular part 82 is used, this invention is not limited to this. The first and second seal rings 8a and 8b have an inner circumferential surface 84 having a width t6 in the direction of the center line 20 of the cylindrical chamber 21 and an outer circumferential surface 85 having a width t7 in the direction of the center line 20 of the cylindrical chamber 21 , As long as it is provided. For example, it may be an annular member having a rectangular cross-section including the inner circumferential surface 84 and the outer circumferential surface 85.
また、上記の実施の形態では、第一、第二シールリング8a、8bの内周面84の幅t6を外周面85の幅t7より狭くして、内周面84において相手面との摺動を生じさせている。しかし、本発明はこれに限定されない。例えば、第一、第二シールリング8a、8bの外周面85の幅t7を内周面84の幅t6より狭くして、外周面85において相手面との摺動を生じさせてもよい。あるいは、第一、第二シールリング8a、8bの内周面84の幅t6と外周面85の幅t7とを同じにして、内周面84および外周面85の両方において相手面との摺動を生じさせてもよい。
Further, in the above embodiment, the width t6 of the inner circumferential surface 84 of the first and second seal rings 8a and 8b is made narrower than the width t7 of the outer circumferential surface 85, and the inner circumferential surface 84 slides against the mating surface. It is causing However, the present invention is not limited to this. For example, the width t7 of the outer peripheral surface 85 of the first and second seal rings 8a and 8b may be smaller than the width t6 of the inner peripheral surface 84 to cause the outer peripheral surface 85 to slide with the mating surface. Alternatively, with the width t6 of the inner peripheral surface 84 of the first and second seal rings 8a and 8b equal to the width t7 of the outer peripheral surface 85, sliding with the mating surface is performed on both the inner peripheral surface 84 and the outer peripheral surface 85 May occur.
また、上記の実施の形態では、第一、第二シールリング8a、8bの内周面84にグリース溝86を円周方向に形成して、このグリース溝86にグリースを充填している。しかし、本発明はこれに限定されない。相手面と摺動する、第一、第二シールリング8a、8bの内周面84および外周面85の少なくとも一方に、グリース溝を円周方向に形成して、このグリース溝にグリースを充填すればよい。
Further, in the above embodiment, the grease grooves 86 are formed in the circumferential direction on the inner peripheral surfaces 84 of the first and second seal rings 8a and 8b, and the grease grooves 86 are filled with the grease. However, the present invention is not limited to this. A grease groove is formed in the circumferential direction on at least one of the inner peripheral surface 84 and the outer peripheral surface 85 of the first and second seal rings 8a and 8b which slide with the mating surface, and the grease groove is filled with the grease. Just do it.
また、上記の実施の形態では、第一、第二シールリング8a、8bの内周面84および外周面85を、円筒室21の中心線20の方向において平坦な面としているが、本発明はこれに限定されない。第一、第二シールリング8a、8bの内周面84および外周面85は、円筒室21の中心線20の方向に幅を有するものであればよい。
In the above embodiment, the inner peripheral surface 84 and the outer peripheral surface 85 of the first and second seal rings 8a and 8b are flat in the direction of the center line 20 of the cylindrical chamber 21, but the present invention It is not limited to this. The inner circumferential surface 84 and the outer circumferential surface 85 of the first and second seal rings 8 a and 8 b may have a width in the direction of the center line 20 of the cylindrical chamber 21.
図11(A)は、第一、第二シールリング8a、8bの変形例8’a、8’bの正面図であり、図11(B)は、図11(A)に示す変形例8’a、8’bのI-I断面図であり、図11(C)は、図11(B)に示す変形例8’a、8’bのG部拡大図である。
FIG. 11 (A) is a front view of modified examples 8'a and 8'b of the first and second seal rings 8a and 8b, and FIG. 11 (B) is a modified example 8 shown in FIG. 11 (A). FIG. 11 (C) is an enlarged view of a portion G of the modified example 8'a, 8'b shown in FIG. 11 (B).
この変形例8’a、8’bは、第一、第二シールリング8a、8bと同様、ニトリルブタジエンゴム等の弾性体で形成された円環状部材であり、第一シールリング8aの変形例8’aにおいては、ロータ3のロータ本体31の下端部33aの外径d4より小さな内径d1と、ケース2の円筒室21の貫通孔23の内径(段差221の外径)d3より大きな外径d2と、を有し、第二シールリング8bの変形例8’bにおいては、ロータ3のロータ本体31の上端部33bの外径d5より小さな内径d1と、蓋6の貫通孔60の内径(段差65の外径)d6より大きな外径d2と、を有する。また、この変形例8’a、8’bは、中心線80の方向に幅t6を有する内周面84’と、中心線80の方向に幅t7を有する外周面85’と、を有する。ここでは、内周面84’の幅t6および外周面85’の幅t7を同じにしているが、両者を異ならせてもよい。
Like the first and second seal rings 8a and 8b, the modifications 8'a and 8'b are annular members formed of an elastic body such as nitrile butadiene rubber, and the modifications of the first seal ring 8a. In 8'a, the outer diameter is larger than the inner diameter d1 smaller than the outer diameter d4 of the lower end 33a of the rotor body 31 of the rotor 3 and the inner diameter d3 of the through hole 23 of the cylindrical chamber 21 of the case 2 (the outer diameter of the step 221). and in the modified example 8 ′ b of the second seal ring 8 b, the inner diameter d 1 smaller than the outer diameter d 5 of the upper end portion 33 b of the rotor body 31 of the rotor 3 and the inner diameter of the through hole 60 of the lid 6 The outer diameter d2 is larger than the outer diameter d6 of the step 65). Further, modifications 8'a and 8'b have an inner circumferential surface 84 'having a width t6 in the direction of center line 80 and an outer circumferential surface 85' having a width t7 in the direction of center line 80. Here, the width t6 of the inner circumferential surface 84 'and the width t7 of the outer circumferential surface 85' are the same, but both may be different.
内周面84’は、ケース2の円筒室21の中心線20と一致する中心線80の方向において、変形例8’a、8’bの径方向の幅t10の半分よりも長い半径r1を有する円弧状の面であり、第一シールリング8aの変形例8’aにおいてはロータ3のロータ本体31の下端部33aの外周面34に圧接し、第二シールリング8bの変形例8’bにおいてはロータ3のロータ本体31の上端部33bの外周面34に圧接する。同様に、外周面85’は、中心線80の方向において、変形例8’a、8’bの径方向の幅t10の半分よりも長い半径r2を有する円弧状の面であり、第一シールリング8aの変形例8’aにおいてはケース2の円筒室21の貫通孔23の内周面220に圧接し、第二シールリング8bの変形例8’bにおいては蓋6の貫通孔60の内周面64に圧接する。
The inner circumferential surface 84 'has a radius r1 longer than half the radial width t10 of the modified examples 8'a and 8'b in the direction of the center line 80 coinciding with the center line 20 of the cylindrical chamber 21 of the case 2. In the modified example 8'a of the first seal ring 8a, it is in pressure contact with the outer peripheral surface 34 of the lower end portion 33a of the rotor body 31 of the rotor 3, and the modified example 8'b of the second seal ring 8b In this case, the outer peripheral surface 34 of the upper end portion 33 b of the rotor body 31 of the rotor 3 is in pressure contact. Similarly, the outer peripheral surface 85 'is an arc-shaped surface having a radius r2 longer than half the radial width t10 of the modified examples 8'a and 8'b in the direction of the center line 80, and the first seal In the modified example 8'a of the ring 8a, the inner peripheral surface 220 of the through hole 23 of the cylindrical chamber 21 of the case 2 is in pressure contact, and in the modified example 8'b of the second seal ring 8b, the inside of the through hole 60 of the lid 6 The pressure is applied to the circumferential surface 64.
このような構成にした場合でも、内周面84’および外周面85’の曲率を変形例8’a、8’bと代替可能なOリングに比べて小さくすることができる。したがって、変形例8’a、8’bが径方向に弾性変形した場合における内周面84’および外周面85’のそれぞれと相手面との接触面積の変化を抑制することができ、シール性を向上させることができる。
Even in such a configuration, the curvatures of the inner circumferential surface 84 'and the outer circumferential surface 85' can be made smaller than O-rings that can be substituted for the modified examples 8'a and 8'b. Therefore, it is possible to suppress a change in the contact area between each of the inner peripheral surface 84 'and the outer peripheral surface 85' and the other surface when the modified examples 8'a and 8'b are elastically deformed in the radial direction Can be improved.
また、上記の実施の形態では、円筒室21に一対の仕切り部25を設けるとともに、ロータ3に一対のベーン32を設けた場合を例にとり説明した。しかし、本発明はこれに限定されない。円筒室21に形成された仕切り部25およびロータ3に形成されたベーン32が同数であれば、1または3以上形成されていてもよい。
Further, in the above embodiment, the case where the pair of partition portions 25 is provided in the cylindrical chamber 21 and the pair of vanes 32 is provided in the rotor 3 has been described as an example. However, the present invention is not limited to this. As long as the partitions 25 formed in the cylindrical chamber 21 and the vanes 32 formed in the rotor 3 have the same number, one or three or more may be formed.
また、上記の実施の形態では、ベーン32に装着されたバルブシール5に、ベーン32に形成された流路36を開閉する逆止弁の機能を持たせているが、本発明はこれに限定されない。ロータ3が円筒室21に対して相対的に第一回転方向R1に回転すると、ベーン32に形成された流路36を塞ぎ、ロータ3が円筒室21に対して相対的に第二回転方向R2に回転すると、ベーン32に形成された流路36を開放する逆止弁を、バルブシール5とは別個に設けてもよい。
In the above embodiment, the valve seal 5 mounted on the vane 32 has the function of a check valve for opening and closing the flow passage 36 formed in the vane 32. However, the present invention is limited thereto I will not. When the rotor 3 rotates relative to the cylindrical chamber 21 in the first rotational direction R1, the flow path 36 formed in the vane 32 is closed, and the rotor 3 relative to the cylindrical chamber 21 in the second rotational direction R2 The non-return valve may be provided separately from the valve seal 5 to open the flow path 36 formed in the vane 32 when it rotates.
また、上記の実施の形態では、ベーン32に、ロータ3の回転方向に沿ってベーン32の両側面37a、37bを貫く流路36を形成しているが、本発明はこれに限定されない。ベーン32に代えて、あるいはベーン32とともに、仕切り部25に、ロータ3の回転方向に沿って仕切り部25の両側面を貫く流路を形成してもよい。この場合、ロータ3が円筒室21に対して相対的に第一回転方向R1に回転すると、仕切り部25に形成された流路を塞ぎ、ロータ3が円筒室21に対して相対的に第二回転方向R2に回転すると、仕切り部25に形成された流路を開放する逆止弁を設けてもよい。
Moreover, although the flow path 36 which penetrates the both sides 37a and 37b of the vane 32 in the said embodiment along the rotation direction of the rotor 3 is formed in the vane 32, this invention is not limited to this. Instead of the vanes 32, or together with the vanes 32, flow paths may be formed in the partition 25 along both sides of the partition 25 along the rotational direction of the rotor 3. In this case, when the rotor 3 is rotated relative to the cylindrical chamber 21 in the first rotational direction R1, the flow path formed in the partition 25 is closed, and the rotor 3 is relatively rotated relative to the cylindrical chamber 21. When rotating in the rotational direction R2, a check valve may be provided that opens the flow path formed in the partition 25.
なお、仕切り部25に流路を形成する場合、バルブシール5と同様の機能を有するシール材、すなわち、仕切り部25の内周縁の周方向幅より長い幅を有する底部と、底部の一方の端部に一体的に形成され、仕切り部25に形成された流路の径方向の幅より長い幅を有する第一脚部と、底部の他方の端部に一体的に形成され、仕切り部25に形成された流路の径方向の幅より短い幅を有する第二脚部と、を有するシール材を仕切り部25に装着してもよい。そして、ロータ3が円筒室21に対して相対的に第一回転方向R1に回転すると、シール材の第一脚部が仕切り部25の一方の側面と当接して、仕切り部25に形成された流路を塞ぎ、ロータ3が円筒室21に対して相対的に第二回転方向R2に回転すると、シール材の第一脚部が仕切り部25の一方の側面から離れ、第二脚部が仕切り部25の他方の側面に当接して、仕切り部25に形成された流路を開放する。
When the flow path is formed in the partition 25, the sealing material having the same function as the valve seal 5, that is, the bottom having a width longer than the circumferential width of the inner peripheral edge of the partition 25, and one end of the bottom The first leg is integrally formed with the first portion and has a width longer than the radial width of the flow path formed in the partition 25, and the other end of the bottom is integrally formed with the partition 25 A sealing material having a second leg portion having a width shorter than the radial width of the formed flow path may be attached to the partition portion 25. Then, when the rotor 3 rotates relative to the cylindrical chamber 21 in the first rotational direction R1, the first leg of the seal material abuts on one side surface of the partition 25 and is formed in the partition 25 When the flow path is closed and the rotor 3 is rotated relative to the cylindrical chamber 21 in the second rotational direction R2, the first leg of the seal member is separated from one side of the partition 25, and the second leg is partitioned It abuts on the other side surface of the portion 25 to open the flow path formed in the partition portion 25.
また、ベーン32に流路36を形成しない場合、バルブシール5は、ベーン32の先端面35と円筒室21の内周面24との隙間を塞ぐことができるものであれば、どのような形状のものでもよい。また、バルブシール5を省略してもかまわない。
When the flow passage 36 is not formed in the vane 32, the valve seal 5 may have any shape as long as it can close the gap between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21. It may be Also, the valve seal 5 may be omitted.
また、上記の実施の形態では、円筒室21の内周面24の開口側28に雌ネジ部27を形成するとともに、蓋6の外周面61にこの雌ネジ部27と螺合する雄ネジ部62を形成することにより、蓋6をケース2に取り付けている。しかし、本発明はこれに限定されない。例えば、蓋6をケース2にボルトで取り付けてもよいし、リベットで取り付けてもよい。あるいは、溶接、接着剤等により取り付けてもかまわない。
In the above embodiment, the female screw portion 27 is formed on the opening side 28 of the inner peripheral surface 24 of the cylindrical chamber 21, and the male screw portion screwed with the female screw portion 27 on the outer peripheral surface 61 of the lid 6. The lid 6 is attached to the case 2 by forming 62. However, the present invention is not limited to this. For example, the lid 6 may be bolted to the case 2 or riveted. Alternatively, they may be attached by welding, an adhesive or the like.
また、上記の実施の形態では、外部からロータ3に回転力を加えることにより、ロータ3をケース2の円筒室21に対して相対的に回転させている。しかし、本発明はこれに限定されない。外部からケース2に回転力を加えることにより、ロータ3をケース2の円筒室21に対して相対的に回転させてもよい。
In the above embodiment, the rotor 3 is rotated relative to the cylindrical chamber 21 of the case 2 by applying a rotational force to the rotor 3 from the outside. However, the present invention is not limited to this. The rotor 3 may be rotated relative to the cylindrical chamber 21 of the case 2 by applying a rotational force to the case 2 from the outside.
また、上記の実施の形態では、ロータ3が円筒室21に対して相対的に第一回転方向R1に回転した場合に、ロータ3が円筒室21に対して相対的に第二回転方向R2に回転した場合よりも強い制動トルクを発生させる、いわゆる一方向性のロータリダンパを例にとり説明した。しかし、本発明はこれに限定されない。本発明は、第一回転方向R1および第二回転方向R2の両方向において、ベーン32あるいは仕切り部25に形成された流路を流れる粘性流体の移動抵抗(流路を介した粘性流体の移動の困難性)に応じた制動トルクを発生させる、いわゆる双方向性のロータリダンパにも適用可能である。この場合、バルブシール5に逆止弁の機能は不要である。バルブシール5は、ベーン32の先端面35と円筒室21の内周面24との隙間を塞ぐことができるものであればよい。また、バルブシール5を省略してもかまわない。
In the above embodiment, when the rotor 3 rotates in the first rotational direction R1 relative to the cylindrical chamber 21, the rotor 3 in the second rotational direction R2 relative to the cylindrical chamber 21. A so-called one-way rotary damper that generates a braking torque stronger than that in the case of rotation has been described as an example. However, the present invention is not limited to this. According to the present invention, the movement resistance of the viscous fluid flowing in the flow path formed in the vane 32 or the partition 25 in both the first rotational direction R1 and the second rotational direction R2 (the movement of the viscous fluid through the flow path is difficult Can be applied to a so-called bidirectional rotary damper that generates a braking torque according to the In this case, the valve seal 5 does not require the function of the check valve. The valve seal 5 only needs to be able to close the gap between the tip end surface 35 of the vane 32 and the inner peripheral surface 24 of the cylindrical chamber 21. Also, the valve seal 5 may be omitted.
また、上記の実施の形態では、粘性流体の移動を制限することにより、外部から加えられた回転力に対して制動トルクを発生させるロータリダンパ1を例にとり説明した。しかしながら、本発明はこれに限定されない。本発明は、粘性流体の移動を制限することにより、外力に対して制動力を発生させるダンパに広く適用可能である。
Further, in the above embodiment, the rotary damper 1 which generates the braking torque with respect to the rotational force applied from the outside by limiting the movement of the viscous fluid has been described as an example. However, the present invention is not limited to this. The present invention is widely applicable to a damper that generates a braking force against an external force by limiting the movement of a viscous fluid.
図12(A)は、本発明の他の実施の形態に係る直動式ダンパ9の側面図であり、図12(B)は、図12(A)に示す直動式ダンパ9のJ-J断面図である。
FIG. 12 (A) is a side view of a direct acting damper 9 according to another embodiment of the present invention, and FIG. 12 (B) is a side view of the direct acting damper 9 shown in FIG. 12 (A). It is J sectional drawing.
本実施の形態に係る直動式ダンパ9は、高さ調整機能付きの椅子、可動棚等、移動体の直線運動を制動することが必要とされる装置に利用される。図示するように、直動式ダンパ9は、オイル、シリコーン等の粘性流体(不図示)を保持する流体保持室を構成するケース920および蓋960と、流体保持室に対して中心線902の方向に相対的に直線移動可能に流体保持室に収容されたシャフト930と、を備えている。
The linear motion damper 9 according to the present embodiment is used for a chair with a height adjustment function, a movable shelf, and other devices that are required to brake the linear motion of a moving object. As shown, the linear motion damper 9 includes a case 920 and a lid 960 which constitute a fluid holding chamber for holding a viscous fluid (not shown) such as oil and silicone, and the direction of the center line 902 with respect to the fluid holding chamber. And a shaft 930 accommodated in the fluid holding chamber so as to be linearly movable relative thereto.
ケース920内には、一端が開口した円筒室(底付き円筒状の空間)921が形成されており、この円筒室921の底部922には、シャフト930挿入用の挿入穴923が形成されている。この挿入穴923には、第一シールリング980aおよび第一ブッシュ990aが装着され、シャフト930は、後述するシャフト本体931の一方の端部933aがこの第一シールリング980aおよび第一ブッシュ990aが装着された挿入穴923に挿入されることにより、シャフト930の中心線903が円筒室921の中心線902と一致するように、円筒室921内に収容される。
In the case 920, a cylindrical chamber (a cylindrical space with a bottom) 921 having one end opened is formed, and an insertion hole 923 for insertion of the shaft 930 is formed in the bottom 922 of the cylindrical chamber 921. . The first seal ring 980a and the first bush 990a are mounted in the insertion hole 923, and the shaft 930 is mounted at one end 933a of the shaft main body 931 described later on the first seal ring 980a and the first bush 990a. By being inserted into the insertion hole 923, the shaft 930 is accommodated in the cylindrical chamber 921 so that the center line 903 of the shaft 930 coincides with the center line 902 of the cylindrical chamber 921.
挿入穴923の内周面929には、第一シールリング980aおよび第一ブッシュ990aを装着するための装着部927が段付き円環溝状に形成されている。また、挿入穴923の底部925には、エア抜き用の貫通孔926が形成されている。また、円筒室921の内周面924の開口側928には、螺合、接着、溶接、ネジ留め、ビス留め等により、蓋960が取り付けられる。
On an inner circumferential surface 929 of the insertion hole 923, a mounting portion 927 for mounting the first seal ring 980a and the first bush 990a is formed in a stepped annular groove shape. Further, in the bottom 925 of the insertion hole 923, a through hole 926 for air removal is formed. Further, a lid 960 is attached to the opening side 928 of the inner circumferential surface 924 of the cylindrical chamber 921 by screwing, bonding, welding, screwing, screwing, or the like.
シャフト930は、円柱状のシャフト本体931と、シャフト本体931の中央付近に形成されたフランジ932と、を備えている。
The shaft 930 includes a cylindrical shaft body 931 and a flange 932 formed near the center of the shaft body 931.
フランジ932は、シャフト本体931の中央付近において、シャフト本体931の外周面934から径方向外方へ張り出し、先端面935がケース920の円筒室921の内周面924と近接して、円筒室921を仕切る。フランジ932は、シャフト930の中心線903方向の直線運動に伴い、フランジ932によって仕切られた円筒室921内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段を構成する。また、フランジ932には、シャフト930の中心線903方向に沿ってフランジ932の両側面937a、937b間を貫く流路936が形成されている。流路936には、シャフト930が円筒室921の中心線902に沿って第一移動方向L1に移動すると、流路936を閉門し、第一移動方向L1の反対方向である第二移動方向L2に移動すると、流路936を開門する逆止弁970が取り付けられている。また、フランジ932の外周面935は、ケース920の円筒室921の内周面924との間に、円筒室921に充填された粘性流体の流路として機能する隙間g’を形成する。
The flange 932 protrudes radially outward from the outer peripheral surface 934 of the shaft main body 931 near the center of the shaft main body 931, and the tip end surface 935 approaches the inner peripheral surface 924 of the cylindrical chamber 921 of the case 920. Partition The flange 932 forms a capacity changing means for compressing one area in the cylindrical chamber 921 partitioned by the flange 932 and extending the other area in accordance with the linear movement of the shaft 930 in the direction of the center line 903. Further, in the flange 932, a flow path 936 is formed along the direction of the center line 903 of the shaft 930 and between the side surfaces 937a and 937b of the flange 932. When the shaft 930 moves in the first movement direction L1 along the center line 902 of the cylindrical chamber 921 in the flow path 936, the flow path 936 is closed, and a second movement direction L2 opposite to the first movement direction L1. The valve 970 is attached to open the flow passage 936. Further, the outer peripheral surface 935 of the flange 932 forms a gap g ′ that functions as a flow path of the viscous fluid filled in the cylindrical chamber 921 between the outer peripheral surface 935 and the inner peripheral surface 924 of the cylindrical chamber 921 of the case 920.
シャフト本体931は、シャフト930の中心線903方向の外力により円筒室921に対して相対的に円筒室921の中心線902の方向に移動する抵抗力発生部材として機能する。シャフト本体931は、一方の端部933a側が、ケース920の円筒室921の底部922に形成された挿入穴923に、円筒室921の中心線902の方向へ移動可能に挿入され、他方の端部933b側が、蓋960の貫通孔961に、円筒室921の中心線902の方向へ移動可能に挿入される。
The shaft main body 931 functions as a resistance generating member that moves in the direction of the center line 902 of the cylindrical chamber 921 relative to the cylindrical chamber 921 by an external force in the direction of the center line 903 of the shaft 930. Shaft body 931 has one end 933a side inserted in insertion hole 923 formed in bottom 922 of cylindrical chamber 921 of case 920 so as to be movable in the direction of center line 902 of cylindrical chamber 921 and the other end The 933 b side is movably inserted into the through hole 961 of the lid 960 in the direction of the center line 902 of the cylindrical chamber 921.
蓋960には、ケース920の円筒室921の底部922に形成された挿入穴923と対向する位置に、流体保持室の開口部として機能するシャフト930挿入用の貫通孔961が形成されている。この貫通孔961には、第二シールリング980bおよび第二ブッシュ990bが装着され、シャフト930は、シャフト本体931の他方の端部933bがこの第二シールリング980bおよび第二ブッシュ990bが装着された貫通孔961に挿入される。また、貫通孔961の内周面964には、第二シールリング980bおよび第二ブッシュ990bを装着するための装着部962が、段付き円環溝状に形成されている。
The lid 960 is formed with a through hole 961 for insertion of a shaft 930 functioning as an opening of the fluid holding chamber at a position opposite to the insertion hole 923 formed in the bottom 922 of the cylindrical chamber 921 of the case 920. The second seal ring 980b and the second bush 990b are mounted in the through hole 961, and the shaft 930 has the other end 933b of the shaft body 931 mounted on the second seal ring 980b and the second bush 990b. It is inserted into the through hole 961. Further, a mounting portion 962 for mounting the second seal ring 980 b and the second bush 990 b is formed in a stepped annular groove shape on the inner peripheral surface 964 of the through hole 961.
第一ブッシュ990aおよび第二ブッシュ990bは、摺動性に優れた材料で形成された円筒状部材であり、第一ブッシュ990aにおいては、シャフト930のシャフト本体931の外周面934と摺接する内周面と、ケース920の円筒室921の挿入穴923の内周面929と当接する外周面と、を有し、第二ブッシュ990bにおいては、シャフト930のシャフト本体931の外周面934と摺接する内周面と、蓋960の貫通孔961の内周面964と当接する外周面と、を有する。
The first bush 990 a and the second bush 990 b are cylindrical members formed of a material having excellent slidability, and the inner circumference of the first bush 990 a slidably contacts the outer peripheral surface 934 of the shaft main body 931 of the shaft 930. And an outer peripheral surface in contact with the inner peripheral surface 929 of the insertion hole 923 of the cylindrical chamber 921 of the case 920, and the second bush 990b is in sliding contact with the outer peripheral surface 934 of the shaft main body 931 of the shaft 930. It has a circumferential surface and an outer circumferential surface in contact with the inner circumferential surface 964 of the through hole 961 of the lid 960.
第一ブッシュ990aおよび第二ブッシュ990bは、例えば、黄銅合金等の金属、または、PTFE、ポリアセタール樹脂、ポリエチレン樹脂、ポリアミド樹脂、ポリフェニレンサルファイド樹脂等の合成樹脂で形成される。あるいは、円筒状のバックメタルの内周面上に、織布あるいは不織布にフェノール樹脂等の合成樹脂を含浸させてなる摺動層が複数層形成された複層摺動部材で形成してもよい。
The first bush 990a and the second bush 990b are formed of, for example, a metal such as a brass alloy or a synthetic resin such as PTFE, polyacetal resin, polyethylene resin, polyamide resin, polyphenylene sulfide resin. Alternatively, a multi-layer sliding member may be formed in which a plurality of sliding layers formed by impregnating a woven or non-woven fabric with a synthetic resin such as phenol resin are formed on the inner peripheral surface of a cylindrical back metal. .
第一、第二シールリング980a、980bは、ニトリルブタジエンゴム等の弾性体で形成された円環状部材である。第一シールリング980aは、円筒室921の中心線902の方向に幅を有し、シャフト本体931の外周面934と摺動可能に圧接する内周面と、円筒室921の中心線902の方向に幅を有し、ケース920の挿入穴923の内周面929に形成された装着部927の溝底と圧接する外周面と、を有する。また、第二シールリング980bは、円筒室921の中心線902の方向に幅を有し、シャフト本体931の外周面934と摺動可能に圧接する内周面と、円筒室921の中心線902の方向に幅を有し、蓋960の貫通孔961の内周面964に形成された装着部962の溝底と圧接する外周面と、を有する。ここで、第一、第二シールリング980a、980bには、例えば、図10に示す第一、第二シールリング8a、8b、あるいは図11に示す第一、第二シールリング8a、8bの変形例8’a、8’b等を用いることができる。
The first and second seal rings 980a and 980b are annular members formed of an elastic material such as nitrile butadiene rubber. The first seal ring 980 a has a width in the direction of the center line 902 of the cylindrical chamber 921 and is in contact with the outer peripheral surface 934 of the shaft body 931 slidably and in the direction of the center line 902 of the cylindrical chamber 921. And an outer peripheral surface pressed against the groove bottom of the mounting portion 927 formed on the inner peripheral surface 929 of the insertion hole 923 of the case 920. The second seal ring 980 b has a width in the direction of the center line 902 of the cylindrical chamber 921, and an inner circumferential surface slidably pressed against the outer circumferential surface 934 of the shaft main body 931, and a center line 902 of the cylindrical chamber 921. And the outer peripheral surface of the mounting portion 962 formed on the inner peripheral surface 964 of the through hole 961 of the lid 960 in pressure contact with the groove bottom. Here, in the first and second seal rings 980a and 980b, for example, the first and second seal rings 8a and 8b shown in FIG. 10 or the deformations of the first and second seal rings 8a and 8b shown in FIG. Examples 8'a, 8'b, etc. can be used.
上記構成の直動式ダンパ9において、シャフト930あるいはケース920に加えられた外力により、シャフト930がケース920の円筒室921に対して相対的に第一移動方向L1に直線移動すると、逆止弁970が流路936を塞ぐ。したがって、円筒室921内に充填された粘性流体の移動が、シャフト930のフランジ932の外周面935と円筒室921の内周面924との隙間g’を介してのみに制限され、フランジ932に対して第一移動方向L1側の領域921a内の粘性流体に対する圧力が高まる。このため、強い制動トルクが発生する。
In the linear motion damper 9 configured as described above, when the shaft 930 moves linearly in the first movement direction L1 relative to the cylindrical chamber 921 of the case 920 by an external force applied to the shaft 930 or the case 920, the check valve 970 blocks channel 936. Therefore, the movement of the viscous fluid filled in the cylindrical chamber 921 is limited only by the gap g ′ between the outer peripheral surface 935 of the flange 932 of the shaft 930 and the inner peripheral surface 924 of the cylindrical chamber 921. In contrast, the pressure on the viscous fluid in the region 921a on the first movement direction L1 side is increased. For this reason, a strong braking torque is generated.
一方、シャフト930あるいはケース920に加えられた外力により、シャフト930がケース920の円筒室921に対して相対的に第二移動方向L2に直線移動すると、逆止弁970が流路936を開放する。したがって、円筒室921内に充填された粘性流体の移動が、フランジ932の外周面935と円筒室921の内周面924との隙間g’に加えて、フランジ932に形成された流路936を介して行われるため、フランジ932に対して第二移動方向L2側の領域921b内の粘性流体に対する圧力は、シャフト930がケース920の円筒室921に対して相対的に第一移動方向L1に移動した場合に比べて高くならない。このため、シャフト930がケース920の円筒室921に対して相対的に第一移動方向L1に移動した場合よりも弱い制動トルクが発生する。
On the other hand, when the shaft 930 moves linearly in the second movement direction L2 relative to the cylindrical chamber 921 of the case 920 by the external force applied to the shaft 930 or the case 920, the check valve 970 opens the flow path 936 . Therefore, in addition to the gap g ′ between the outer peripheral surface 935 of the flange 932 and the inner peripheral surface 924 of the cylindrical chamber 921, the movement of the viscous fluid filled in the cylindrical chamber 921 adds the flow passage 936 formed in the flange 932 Since the pressure is applied to the viscous fluid in the area 921b on the second movement direction L2 side with respect to the flange 932, the shaft 930 moves in the first movement direction L1 relative to the cylindrical chamber 921 of the case 920. Not as high as when Therefore, a braking torque that is weaker than when the shaft 930 moves in the first movement direction L1 relative to the cylindrical chamber 921 of the case 920 is generated.
上記構成の直動式ダンパ9においても、図1に示すロータリダンパ1と同様の効果を奏する。すなわち、直動式ダンパ9では、ケース920の円筒室921の挿入穴923および蓋960の貫通孔961のそれぞれに装着された第一ブッシュ990aおよび第二ブッシュ990bによりシャフト930を摺動可能に保持しているので、第一ブッシュ990aおよび第二ブッシュ990bとともにシャフト930を摺動可能に保持する第一シールリング980aおよび第二シールリング980bの剛性を高くしなくても、シャフト930の軸ずれを抑制することができる。このため、シャフト930の移動に追従して弾性変形するように第一シールリング980aおよび第二シールリング980bの剛性を低くすることができ、これにより、シャフト930と第一シールリング980aおよび第二シールリング980bとの隙間をなくして、ケース920の円筒室921に保持された粘性流体が外部へ漏れる可能性を低減することができる。
Also in the direct acting damper 9 of the above configuration, the same effect as the rotary damper 1 shown in FIG. 1 is obtained. That is, in the linear motion damper 9, the shaft 930 is slidably held by the first bush 990a and the second bush 990b which are attached to the insertion hole 923 of the cylindrical chamber 921 of the case 920 and the through hole 961 of the lid 960 respectively. Since the first seal ring 980a and the second seal ring 980b, which slidably hold the shaft 930 together with the first and second bushes 990a and 990b, do not make the shaft 930 off-axis without increasing its rigidity. It can be suppressed. Therefore, the rigidity of the first seal ring 980a and the second seal ring 980b can be lowered to elastically deform following the movement of the shaft 930, whereby the shaft 930 and the first seal ring 980a and the second By eliminating the gap with the seal ring 980b, the possibility of the viscous fluid held in the cylindrical chamber 921 of the case 920 leaking to the outside can be reduced.
また、直動式ダンパ9では、ケース920の円筒室921の挿入穴923とシャフト930のシャフト本体931の一方の端部933aとの間に、円筒室921の中心線902の方向に平坦な幅を有し、シャフト本体931の外周面934と摺動可能に圧接する内周面と、円筒室921の中心線902の方向に幅を有し、ケース920の挿入穴923の内周面929に形成された装着部927の溝底と圧接する外周面と、を有する第一シールリング980aを配置するとともに、蓋960の貫通孔961とシャフト本体931の他方の端部933bとの間に、円筒室921の中心線902の方向に幅を有し、シャフト本体931の外周面934と摺動可能に圧接する内周面と、円筒室921の中心線902の方向に幅を有し、蓋960の貫通孔961の内周面964に形成された装着部962の溝底と圧接する外周面と、を有する第二シールリング980bを配置している。
In the linear motion damper 9, the width flat in the direction of the center line 902 of the cylindrical chamber 921 between the insertion hole 923 of the cylindrical chamber 921 of the case 920 and one end 933 a of the shaft main body 931 of the shaft 930. And has a width in the direction of the center line 902 of the cylindrical chamber 921 and on the inner circumferential surface 929 of the insertion hole 923 of the case 920. A first seal ring 980a having an outer peripheral surface pressed against the groove bottom of the formed mounting portion 927 is disposed, and a cylinder is provided between the through hole 961 of the lid 960 and the other end 933b of the shaft main body 931. The cover 960 has a width in the direction of the center line 902 of the chamber 921 and has a width in the direction of the center line 902 of the cylindrical chamber 921. Penetration of It is arranged and the outer circumferential surface of the groove bottom and pressing the mounting portion 962 inner peripheral surface 964 formed in the hole 961, the second seal ring 980b having.
このため、第一、第二シールリング980a、980bの代わりに断面円形状のOリングを用いた場合に比べ、シャフト930が軸ずれを起こして、第一、第二シールリング980a、980bが径方向に弾性変形した場合における、第一シールリング980aとシャフト本体931の一方の端部933aとの接触面積、第一シールリング980aと円筒室921の挿入穴923に形成された装着部927の溝底との接触面積、第二シールリング980bとシャフト本体931の他方の端部933bとの接触面積、および、第二シールリング980bと蓋960の貫通孔961に形成された装着部962の溝底との接触面積の変化を抑制することができる。これにより、円筒室921の挿入穴923とシャフト本体931の一方の端部933aとの間、および、蓋960の貫通孔961とシャフト本体931の他方の端部933bとの間のシール性が安定して、円筒室921内に充填された粘性流体がこれらの隙間から漏れる可能性を低減することができる。
Therefore, as compared with the case where an O-ring having a circular cross-section is used instead of the first and second seal rings 980a and 980b, the shaft 930 is offset and the first and second seal rings 980a and 980b have diameters. The contact area between the first seal ring 980a and one end 933a of the shaft main body 931 when elastically deformed in the direction, and the groove of the mounting portion 927 formed in the insertion hole 923 of the first seal ring 980a and the cylindrical chamber 921. The contact area with the bottom, the contact area between the second seal ring 980 b and the other end 933 b of the shaft main body 931, and the groove bottom of the mounting portion 962 formed in the through hole 961 of the second seal ring 980 b and the lid 960. It is possible to suppress the change in the contact area with the Thereby, the sealability between the insertion hole 923 of the cylindrical chamber 921 and one end 933 a of the shaft main body 931 and between the through hole 961 of the lid 960 and the other end 933 b of the shaft main 931 is stable. Thus, the possibility that the viscous fluid filled in the cylindrical chamber 921 leaks from these gaps can be reduced.
1:ロータリダンパ 2,920:ケース 3:ロータ 4a,990a:第一ブッシュ 4b,990b:第二ブッシュ 5:バルブシール 6,960:蓋 7:Oリング 8a,980a:第一シールリング 8b,980b:第二シールリング 9:直動式ダンパ 21,921:円筒室 22:円筒室21の底部 23:円筒室21の貫通孔 24:円筒室21の内周面 25:仕切り部 26:仕切り部25の先端面 27:雌ネジ部 28:円筒室21の開口側 29:仕切り部25の上面 31:ロータ本体 32:ベーン 33a:ロータ本体31の下端部 33b:ロータ本体31の上端部 34:ロータ本体31の外周面 35:ベーン32の先端面 36,936:流路 37a,37b:ベーン32の側面 38:ロータ本体31の挿入穴 39:ベーン32の上面 40a:第一ブッシュ4aの内周面 40b:第二ブッシュ4bの内周面 41a:第一ブッシュ4aの外周面 41b:第二ブッシュ4bの外周面 50:バルブシール5の底部 51,52:バルブシール5の底部50の端部 53:バルブシール5の第一脚部 54:バルブシール5の第二脚部 60:蓋6の貫通孔 61:蓋6の外周面 62:雄ネジ部 63:蓋6の下面 64:貫通孔60の内周面 65,66:内周面64の段差 67:蓋6の溝 81:内周側円環部 82:外周側円環部 83:連結部 84:内周側円環部81の内周面 85:外周側円環部82の外周面 86:グリース溝 220:貫通孔23の内周面 221,222:内周面220の段差 340a:下端部33aの外周面34の段差 340b:上端部33bの外周面34の段差 922:円筒室921の底部 923:挿入穴 924:円筒室921の内周面 925:挿入穴923の底部 926:エア抜き用の貫通孔 927:第一シールリング980aの装着部 928:円筒室921の開口側 929:挿入穴923の内周面 930:シャフト 931:シャフト本体 932:フランジ 933a、933b:シャフト本体931の端部 934:シャフト本体931の外周面 935:フランジ932の外周面 937a,937b:フランジ932の側面 961:蓋960の貫通孔 962:第二シールリング980bの装着部 964:貫通孔961の内周面 970:逆止弁
1: Rotary damper 2, 920: Case 3: Rotor 4a, 990a: First bush 4b, 990b: Second bush 5: Valve seal 6, 960: Lid 7: O ring 8a, 980a: First seal ring 8b, 980b : Second seal ring 9: linear motion damper 21, 921: cylindrical chamber 22: bottom of cylindrical chamber 23: through hole 24 of cylindrical chamber 21: inner circumferential surface of cylindrical chamber 25: partition 26: partition 25 End face 27: female screw 28: opening side of cylindrical chamber 21 29: upper surface of partition 25 31: rotor main body 32: vane 33a: lower end of rotor main body 33b: upper end of rotor main body 34: rotor main body 31 outer peripheral surface 35: tip end surface of the vane 32 36, 936: flow path 37a, 37b: side surface of the vane 32 38: of the rotor main body 31 Entry hole 39: upper surface of vane 32 40a: inner circumferential surface 40b of first bush 4a: inner circumferential surface of second bush 4b 41a: outer circumferential surface of first bush 4a 41b: outer circumferential surface of second bush 4b 50: valve seal 5 bottom 51, 52: end of bottom 50 of valve seal 5 53: first leg of valve seal 54: second leg of valve seal 60: through hole of lid 6: outer peripheral surface of lid 6 62: Male thread portion 63: Lower surface 64 of lid 6: Inner circumferential surface 65 of the through hole 60, 66: Step difference of inner circumferential surface 64 67: Groove of lid 6 81: Inner circumferential ring 82: Outer circumferential ring Part 83: Connection part 84: Inner peripheral surface of inner peripheral side annular part 81: Outer peripheral surface of outer peripheral side annular part 82: Grease groove 220: Inner peripheral surface of through hole 23 221, 222: Inner peripheral surface 220 Step 340a: outer peripheral surface 34 of the lower end 33a Step 340b: Step on outer peripheral surface 34 of upper end 33b 922: bottom of cylindrical chamber 921: insertion hole 924: inner peripheral surface of cylindrical chamber 925: bottom of insertion hole 923 926: through hole for air venting 927: first A mounting portion of seal ring 980a 928: open side of cylindrical chamber 921: inner peripheral surface of insertion hole 923: shaft 931: shaft body 932: flange 933a, 933b: end of shaft body 931 934: shaft body 931 Outer peripheral surface 935: Outer peripheral surface of flange 932 937a, 937b: side surface of flange 932 961: through hole of lid 960 962: mounting portion of second seal ring 980b 9: inner peripheral surface of through hole 961 970: check valve
1: Rotary damper 2, 920: Case 3: Rotor 4a, 990a: First bush 4b, 990b: Second bush 5: Valve seal 6, 960: Lid 7: O ring 8a, 980a: First seal ring 8b, 980b : Second seal ring 9: linear motion damper 21, 921: cylindrical chamber 22: bottom of cylindrical chamber 23: through hole 24 of cylindrical chamber 21: inner circumferential surface of cylindrical chamber 25: partition 26: partition 25 End face 27: female screw 28: opening side of cylindrical chamber 21 29: upper surface of partition 25 31: rotor main body 32: vane 33a: lower end of rotor main body 33b: upper end of rotor main body 34: rotor main body 31 outer peripheral surface 35: tip end surface of the vane 32 36, 936: flow path 37a, 37b: side surface of the vane 32 38: of the rotor main body 31 Entry hole 39: upper surface of vane 32 40a: inner circumferential surface 40b of first bush 4a: inner circumferential surface of second bush 4b 41a: outer circumferential surface of first bush 4a 41b: outer circumferential surface of second bush 4b 50: valve seal 5 bottom 51, 52: end of bottom 50 of valve seal 5 53: first leg of valve seal 54: second leg of valve seal 60: through hole of lid 6: outer peripheral surface of lid 6 62: Male thread portion 63: Lower surface 64 of lid 6: Inner circumferential surface 65 of the through hole 60, 66: Step difference of inner circumferential surface 64 67: Groove of lid 6 81: Inner circumferential ring 82: Outer circumferential ring Part 83: Connection part 84: Inner peripheral surface of inner peripheral side annular part 81: Outer peripheral surface of outer peripheral side annular part 82: Grease groove 220: Inner peripheral surface of through hole 23 221, 222: Inner peripheral surface 220 Step 340a: outer peripheral surface 34 of the lower end 33a Step 340b: Step on outer peripheral surface 34 of upper end 33b 922: bottom of cylindrical chamber 921: insertion hole 924: inner peripheral surface of cylindrical chamber 925: bottom of insertion hole 923 926: through hole for air venting 927: first A mounting portion of seal ring 980a 928: open side of cylindrical chamber 921: inner peripheral surface of insertion hole 923: shaft 931: shaft body 932: flange 933a, 933b: end of shaft body 931 934: shaft body 931 Outer peripheral surface 935: Outer peripheral surface of flange 932 937a, 937b: side surface of flange 932 961: through hole of lid 960 962: mounting portion of second seal ring 980b 9: inner peripheral surface of through hole 961 970: check valve
Claims (18)
- 粘性流体の移動を制限することにより、外力に対して制動力を発生させるダンパであって、
開口部を有し、前記粘性流体を保持する流体保持室と、
前記流体保持室の前記開口部に挿入され、前記外力により前記流体保持室に対して相対的に移動する抵抗力発生部材と、
前記流体保持室内を仕切るとともに、前記流体保持室に対する前記抵抗力発生部材の相対的な移動に伴い、仕切られた前記流体保持室内の一方の領域を圧縮し、かつ他方の領域を伸張する容量変更手段と、
前記容量変更手段によって仕切られた前記流体保持室内の領域間を連結する流路と、
前記流体保持室の前記開口部に装着され、前記流体保持室の前記開口部に挿入された前記抵抗力発生部材を摺動可能に保持するブッシュと、
前記ブッシュに保持された前記抵抗力発生部材と前記流体保持室の前記開口部との間に配置された円環状の弾性部材と、を備え、
前記弾性部材は、
前記流体保持室の中心線方向に幅を有し、前記抵抗力発生部材に圧接する内周面と、
前記流体保持室の中心線方向に幅を有し、前記流体保持室に圧接する外周面と、を備えている
ことを特徴とするダンパ。 A damper that generates a braking force against an external force by restricting the movement of a viscous fluid,
A fluid holding chamber having an opening and holding the viscous fluid;
A resistance generating member inserted into the opening of the fluid holding chamber and moved relative to the fluid holding chamber by the external force;
A capacity change which partitions the fluid holding chamber and compresses one region in the partitioned fluid holding chamber and extends the other region with relative movement of the resistance generating member with respect to the fluid holding chamber Means,
A flow path connecting between the regions in the fluid holding chamber partitioned by the volume changing means;
A bush attached to the opening of the fluid holding chamber and slidably holding the resistance generating member inserted into the opening of the fluid holding chamber;
And an annular elastic member disposed between the resistance generating member held by the bush and the opening of the fluid holding chamber.
The elastic member is
An inner circumferential surface having a width in a direction of a center line of the fluid holding chamber and in pressure contact with the resistance generating member;
A damper having a width in a direction of a center line of the fluid holding chamber, and an outer circumferential surface pressed against the fluid holding chamber. - 請求項1に記載のダンパであって、
前記ブッシュは、
前記ダンパの軸方向において、前記流体保持室に対して前記弾性部材よりも外側に配置されている
ことを特徴とするダンパ。 The damper according to claim 1, wherein
The bush is
A damper characterized in that it is disposed outside the elastic member with respect to the fluid holding chamber in the axial direction of the damper. - 請求項1に記載のダンパであって、
前記ブッシュは、
前記ダンパの軸方向において、前記流体保持室に対して前記弾性部材よりも内側に配置されている
ことを特徴とするダンパ。 The damper according to claim 1, wherein
The bush is
A damper characterized in that it is disposed inside the elastic member with respect to the fluid holding chamber in the axial direction of the damper. - 請求項1ないし3のいずれか一項に記載のダンパであって、
前記弾性部材の前記内周面および前記外周面の少なくとも一方は、
前記流体保持室の中心線方向において平坦面である
ことを特徴とするダンパ。 The damper according to any one of claims 1 to 3, wherein
At least one of the inner peripheral surface and the outer peripheral surface of the elastic member is
A damper having a flat surface in a direction of a center line of the fluid holding chamber. - 請求項1ないし3のいずれか一項に記載のダンパであって、
前記弾性部材の前記内周面および前記外周面の少なくとも一方は、
前記流体保持室の中心線方向において、前記弾性部材の径方向の幅の半分よりも長い半径の円弧面である
ことを特徴とするダンパ。 The damper according to any one of claims 1 to 3, wherein
At least one of the inner peripheral surface and the outer peripheral surface of the elastic member is
A damper characterized in that it is a circular arc surface with a radius longer than half of the radial width of the elastic member in the direction of the center line of the fluid holding chamber. - 請求項1ないし5のいずれか一項に記載のダンパであって、
前記弾性部材は、
前記弾性部材の前記内周面および前記外周面の前記流体保持室の中心線方向における一方の幅が、前記弾性部材の前記内周面および前記外周面の前記流体保持室の中心線方向における他方の幅より狭い
ことを特徴とするダンパ。 The damper according to any one of claims 1 to 5, wherein
The elastic member is
The width of one of the inner circumferential surface and the outer circumferential surface of the elastic member in the direction of the center line of the fluid holding chamber is the other width of the inner circumferential surface of the elastic member and the outer circumferential surface in the center line direction of the fluid holding chamber Damper narrower than the width of. - 請求項6に記載のダンパであって、
前記弾性部材の前記内周面の前記流体保持室の中心線方向における幅をa1とし、前記弾性部材の前記外周面の前記流体保持室の中心線方向における幅をa2とした場合に、a2/a1≦3である
ことを特徴とするダンパ。 The damper according to claim 6, wherein
When the width of the inner peripheral surface of the elastic member in the centerline direction of the fluid holding chamber is a1, and the width of the outer peripheral surface of the elastic member in the centerline direction of the fluid holding chamber is a2, a2 / A damper characterized in that a1 ≦ 3. - 請求項1ないし7のいずれか一項に記載のダンパであって、
前記弾性部材は、
前記弾性部材の前記内周面および前記外周面の少なくとも一方に円周方向の溝が少なくとも一つ形成されている
ことを特徴とするダンパ。 The damper according to any one of claims 1 to 7, wherein
The elastic member is
At least one circumferential groove is formed in at least one of the inner peripheral surface and the outer peripheral surface of the elastic member. - 請求項8に記載のダンパであって、
前記少なくとも一つの円周方向の溝の前記流体保持室の中心線方向における幅の合計をb1とし、当該少なくとも一つの円周方向の溝が形成されている前記弾性部材の前記内周面あるいは前記外周面の前記流体保持室の中心線方向における幅をb2とした場合に、0.05≦b1/b2≦0.5である
ことを特徴とするダンパ。 The damper according to claim 8, wherein
The total width of the at least one circumferential groove in the center line direction of the fluid holding chamber is b1, and the inner circumferential surface of the elastic member or the elastic member in which the at least one circumferential groove is formed A damper characterized in that 0.05 ≦ b1 / b2 ≦ 0.5, where b2 is the width of the outer peripheral surface in the center line direction of the fluid holding chamber. - 請求項1ないし9のいずれか一項に記載のダンパであって、
前記弾性部材は、
前記弾性部材の前記内周面を含む断面矩形状の内周側円環部と、
前記弾性部材の前記外周面を含む断面矩形状の外周側円環部と、
前記内周側円環部と前記外周側円環部とを連結する連結部と、を有し、
前記連結部は、
前記流体保持室の中心線方向において、前記内周側円環部および前記外周側円環部より狭い幅を有する
ことを特徴とするダンパ。 A damper according to any one of the preceding claims, wherein
The elastic member is
An inner circumferential ring portion having a rectangular cross section including the inner circumferential surface of the elastic member;
An outer peripheral side annular portion having a rectangular cross section including the outer peripheral surface of the elastic member;
A connecting portion connecting the inner circumferential ring portion and the outer circumferential ring portion;
The connecting portion is
A damper characterized in that the fluid holding chamber has a narrower width than the inner circumferential ring portion and the outer circumferential ring portion in the direction of the center line of the fluid holding chamber. - 請求項10に記載のダンパであって、
前記内周側円環部の前記流体保持室の中心線方向における幅をc1とし、前記外周側円環部の前記流体保持室の中心線方向における幅をc2とし、前記連結部の前記流体保持室の中心線方向における幅をc3した場合に、c3<c1<c2であり、かつ0.3≦c3/c1≦0.95である
ことを特徴とするダンパ。 The damper according to claim 10, wherein
The width of the inner annular portion in the centerline direction of the fluid holding chamber is c1, the width of the outer annular portion in the centerline direction of the fluid holding chamber is c2, and the fluid holding portion of the connecting portion A damper characterized in that c3 <c1 <c2 and 0.3 <c3 / c1 <0.95, where c3 is the width of the chamber in the center line direction. - 請求項1ないし11のいずれか一項に記載のダンパであって、
前記抵抗力発生部材には、
前記流体保持室の前記開口部と対向する外周面に、前記弾性部材および前記ブッシュの軸方向内方への移動を規制する段差が形成されている
ことを特徴とするダンパ。 A damper according to any one of the preceding claims, wherein
The resistance generating member is
A damper characterized in that a step is formed on an outer peripheral surface of the fluid holding chamber opposite to the opening to restrict the axial inward movement of the elastic member and the bush. - 請求項1ないし12のいずれか一項に記載のダンパであって、
前記流体保持室の前記開口部は、
前記抵抗力発生部材と対面する内周面に、前記弾性部材の軸方向外方への移動を規制する段差が形成されている
ことを特徴するダンパ。 A damper according to any one of the preceding claims, wherein
The opening of the fluid holding chamber is
A damper characterized in that a step is formed on the inner peripheral surface facing the resistance force generation member, which restricts the outward movement of the elastic member in the axial direction. - 請求項1ないし13のいずれか一項に記載のダンパであって、
前記流体保持室の前記開口部は、
前記抵抗力発生部材と対面する内周面に、前記ブッシュの軸方向外方への移動を規制する段差が形成されている
ことを特徴するダンパ。 14. A damper according to any one of the preceding claims, wherein
The opening of the fluid holding chamber is
A damper characterized in that a step is formed on an inner circumferential surface facing the resistance force generation member, which restricts the outward movement of the bush in the axial direction. - 請求項1ないし14のいずれか一項に記載のダンパであって、
前記抵抗力発生部材が前記流体保持室の中心線に沿って前記流体保持室に対して相対的に第一移動方向に直線移動した場合、あるいは、前記抵抗力発生部材が前記流体保持室に対して相対的に第一回転方向に回転移動した場合に、前記流路を閉門し、前記抵抗力発生部材が前記流体保持室の中心線に沿って前記流体保持室に対して相対的に前記第一移動方向の逆方向である第二移動方向に直線移動した場合、あるいは、前記抵抗力発生部材が前記流体保持室に対して相対的に前記第一回転方向の逆回転方向である第二回転方向に回転移動した場合に、前記流路を開門する逆止弁をさらに備える
ことを特徴とするダンパ。 A damper according to any one of the preceding claims, wherein
When the resistance force generating member linearly moves in the first movement direction relative to the fluid holding chamber along the center line of the fluid holding chamber, or the resistance force generating member moves relative to the fluid holding chamber The flow passage is closed in the first rotational direction, and the resistance force generating member closes the flow passage relative to the fluid holding chamber along a center line of the fluid holding chamber. When moving linearly in the second movement direction which is the opposite direction of one movement direction, or the second rotation which is the reverse rotation direction of the first rotation direction relative to the fluid holding chamber A damper characterized by further comprising a check valve which opens the flow passage when rotationally moved in a direction. - 請求項1ないし15のいずれか一項に記載のダンパであって、
前記流体保持室は、
一端が開口した円筒状のケースと、
前記ケースの開口側の端部に取り付けられて前記粘性流体を前記ケース内に封じ込む蓋と、を有し、
前記流体保持室の前記開口部は、
前記ケースの他端および前記蓋の少なくとも一方に形成されている
ことを特徴とするダンパ。 A damper according to any one of the preceding claims, wherein
The fluid holding chamber is
A cylindrical case with an open end,
A lid attached to the open end of the case for sealing the viscous fluid in the case;
The opening of the fluid holding chamber is
A damper characterized in that it is formed on at least one of the other end of the case and the lid. - 請求項1ないし16のいずれか一項に記載のダンパであって、
前記抵抗力発生部材は、
前記流体保持室に挿入され、前記外力として加えられた回転力により、前記流体保持室に対して相対的に回転するように当該流体保持室に収容されたロータ本体であり、
前記容量変更手段は、
前記流体保持室の中心線に沿って当該流体保持室の内周面から径方向内方に突出し、当該流体保持室を仕切る仕切り部と、
前記流体保持室の中心線に沿って前記ロータ本体の外周面から径方向外方に突出し、先端面が前記流体保持室の内周面と近接して、当該流体保持室内を仕切るベーンと、を有する
ことを特徴とするダンパ。 17. A damper according to any one of the preceding claims, wherein
The resistance generating member is
A rotor main body inserted in the fluid holding chamber and housed in the fluid holding chamber so as to rotate relative to the fluid holding chamber by the rotational force applied as the external force,
The capacity changing means is
A partition which protrudes radially inward from an inner circumferential surface of the fluid holding chamber along a center line of the fluid holding chamber, and partitions the fluid holding chamber;
A vane which protrudes radially outward from the outer peripheral surface of the rotor main body along the center line of the fluid holding chamber, and whose tip end surface is close to the inner peripheral surface of the fluid holding chamber to partition the fluid holding chamber; Damper characterized by having. - 請求項17に記載のダンパであって、
前記流路は、
前記容量変更手段の前記仕切り部あるいは前記ベーンに設けられ、当該仕切り部あるいは当該ベーンによって仕切られる前記流体保持室内の領域間を連結する
ことを特徴とするダンパ。 The damper according to claim 17, wherein
The flow path is
A damper, which is provided in the partition portion or the vane of the capacity changing means, and connects the regions in the fluid holding chamber which is partitioned by the partition portion or the vane.
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Also Published As
Publication number | Publication date |
---|---|
JP2019100532A (en) | 2019-06-24 |
US11287008B2 (en) | 2022-03-29 |
US20200318706A1 (en) | 2020-10-08 |
EP3722634A1 (en) | 2020-10-14 |
CN111433487B (en) | 2022-05-17 |
EP3722634A4 (en) | 2021-10-13 |
EP3722634B1 (en) | 2023-08-23 |
CN111433487A (en) | 2020-07-17 |
JP7075749B2 (en) | 2022-05-26 |
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